RU2684248C1 - Systems of connector cushion of carriage roller bearing of railway car - Google Patents

Abstract

FIELD: machine building.SUBSTANCE: invention relates to the field of axle boxes of railway cars. Between the axle box and the axle opening of the side frame of the carriage the axle box adapter and a replacement cushion is installed. Cushion is made of upper and lower rigid plates. Plates are connected by a layer of elastomer. Upper and lower plates are made of a similar shape with the sections bent upwards. On the outer surfaces of the upper and lower plates are made transverse tides, intended for fixation on the side frame and axle box adapter, respectively. Upper and lower plates are movable relative to each other due to the deformation of the elastomer.EFFECT: increase in the speed of the car during the passage of the curves.38 cl, 91 dwg, 3 tbl

Description

CROSS REFERENCE TO RELATED APPLICATIONS

[0001] This patent application claims the priority of U.S. Patent Application No. 15 / 152,860, filed May 12, 2016, entitled "Railcar Truck Roller Bearing Adapter Pad Systems", and US Provisional Application No. 62 / 161,139, filed May 13, 2015, this application is also a partial continuation of US patent application No. 14 / 585,569, filed December 30, 2014, which, in turn, claims the priority of provisional US patent applications, serial numbers 61 / 921,961 and 62 / 065,438 filed December 30, 2013 and October 17, 2014, respectively; and the present patent is also related to US Patent Application No. 14 / 561,897, filed December 5, 2014, US Patent Application No. 14 / 562,005, filed December 5, 2014, and US Patent Application No. 14 / 562,082, filed December 5, 2014 years, for each of which, in turn, claims the priority of provisional US patent applications, serial numbers 61 / 921,961 and 62 / 065,438, filed December 30, 2013 and October 17, 2014, respectively. Descriptions of each of the aforementioned applications are hereby incorporated by reference in their entirety.

FIELD OF THE INVENTION

[0002] The present invention relates to railway carriage bogies and, in particular, to roller bearing adapter systems and adapter pillows, which can improve the stiffness, damping and displacement characteristics to meet both the performance characteristics of the curves and the high-speed performance of the three-element carts of a railway carriage.

BACKGROUND

[0003] The decades-old conventional railroad freight wagon has been a three-piece wagon containing a pair of parallel side frames connected by a transverse mounted crossbar. The nadressornoj beam is supported on the side frames by spring sets consisting of several separate springs. Wheel pairs of the trolley are adopted in bearing adapters located in the front and rear axle boxes in the side frames, so that the axles of the wheelsets are parallel in the transverse or lateral position relative to the two rails. The railway carriage is mounted on the thrust bearing of the nadressornoj beam, which allows rotation of the trolley relative to the carriage. The gaps from the spring sets and side frames to the spring bar allow some movement of the side frames relative to the spring bar around the longitudinal, vertical and transverse or lateral axes.

[0004] For a long time, there was a need to improve the performance of a three-piece trolley. The resistance to lateral and longitudinal loads and the performance of the trolley can be characterized in terms of one or more of the following well-known phenomena.

[0005] “Parallelogram-shaped deformation” occurs when one side frame is moved longitudinally forward relative to the other, so that the front and rear wheelsets remain parallel to each other, but they are not perpendicular to the rails, as happens when a railroad carriage passes a curve. This deformation of the side frames in the shape of a parallelogram is also called skew cart.

[0006] “Wobble” describes an oscillatory sinusoidal longitudinal and transverse movement of wheel pairs that causes the wagon body to swing from side to side. This sinusoidal movement is a harmonic oscillation associated with the conical profile of the wheelset. Although the conical profile contributes to the natural vibration of the wheelset, it is also a major feature that allows the wheelsets to provide a difference in rolling radii and traverse curves. Wobble becomes dangerous when the vibrations reach a resonant frequency. Wobbling most often occurs in the absence of proper alignment of the cart during manufacture, or manifested over time due to various operating conditions, such as wear of the components of the cart. Wobble can also often occur when the car moves at higher speeds. The speed at which the occurrence of wobble is observed is called the “wag threshold”.

[0007] Several attempts have been made to improve the stability of a standard three-element trolley to prevent deformation in the form of a parallelogram and wobble while ensuring that the trolley can have a suitable geometry to match the different distances traveled by the wheels inside and outside the turn, respectively. Further improvement is needed both to meet the requirements for wagging the trolley, and to simultaneously improve the stiffness, damping and displacement characteristics, which provide good performance at high speeds and when passing curves.

SUMMARY OF THE INVENTION

[0008] The present description in a simplified form provides an introduction to some general concepts related to the present invention, which are further described below in the Description of Preferred Embodiments section.

[0009] Aspects of the present invention relate to railcar wagons, roller bearing adapters, and adapter pads.

[0010] In one example of the invention, a roller bearing adapter pad is provided for use with a three-piece trolley having AAR (American Railways Association) geometry, the adapter pad being adapted to interact with the axle box of the side frame. The roller bearing adapter cushion may include a continuous upper plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upward directed portion, the first transverse flange having a first transverse an edge and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, and not reryvnaya top plate having first and second longitudinal edges; a continuous lower plate having a central portion, first and second upwardly extending portions protruding upward from opposing edges of the central portion, a first transverse flange protruding outward from the first upward directed portion, the first transverse flange having a first transverse edge, and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, the continuous lower plate having first and second longitudinal edges; an elastomeric element located between the upper and lower plates. The first transverse edge of the upper plate and the second transverse edge of the upper plate can form a side view bending inward or angled inward from the outer surface of the upper plate to the inner surface of the upper plate in side view, and the first transverse edge of the lower plate and the second transverse edge of the lower plate form or an edge directed at an angle inward from the outer surface of the lower plate to the inner surface of the lower plate in side view. The first longitudinal edge of the upper plate and the second longitudinal edge of the upper plate form a side bend inward or angled inward from the outer surface of the upper plate to the inner surface of the upper plate in a side view, and the first longitudinal edge of the lower plate and the second longitudinal edge of the lower plate form a bend inward or side directed at an angle inward from the outer surface of the bottom plate to the inner surface of the bottom plate in side view. The first transverse edge of the upper plate and the second transverse edge of the upper plate contain curved sections in a plan view, and the first transverse edge of the lower plate and the second transverse edge of the lower plate contain curved sections in a plan view. The elastomeric element extends outward in the transverse direction beyond the first and second transverse edges of the upper and lower plates; and the elastomeric element extends outwardly in the longitudinal direction beyond the first and second longitudinal edges of the upper and lower plates.

[0011] The first transverse edge of the upper plate and the second transverse edge of the upper plate can have a continuous radius in a plan view, measured from a vertical axis at a center point of a central portion of the upper plate, and the first transverse edge of the lower plate and the second transverse edge of the lower plate have a continuous radius of top view, measured from the vertical axis at the center point of the central portion of the bottom plate.

[0012] The elastomeric element can extend outward in the transverse direction beyond the first and second transverse edges of the upper and lower plates by at least 0.05 inches, and the elastomeric element can extend outward in the longitudinal direction beyond the first and second longitudinal edges of the upper and lower plates at least 0.05 inches. An elastomeric element located between the central regions of the upper and lower plates may have a substantially uniform thickness.

[0013] In another example, a roller bearing adapter cushion system is disclosed configured for use with a three-piece trolley having AAR geometry. The roller bearing adapter cushion system may include a roller bearing adapter configured to cooperate with the roller bearing, the roller bearing adapter comprising: a convex upper surface; a lower surface configured to interact with a roller bearing; and first and second vertical shoulders that protrude upward from opposing transverse edges of the upper surface. The roller bearing adapter pillow system may also include an adapter pillow cooperating with the roller bearing adapter and configured to interact with the axle box of the side frame. The adapter cushion may include a continuous upper plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upwardly directed portion, the first transverse flange having a first transverse edge, and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, wherein the continuous upper ina has first and second longitudinal edges; a continuous lower plate having a central portion, first and second upwardly extending portions protruding upward from opposing edges of the central portion, a first transverse flange protruding outward from the first upward directed portion, the first transverse flange having a first transverse edge, and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, the continuous lower plate having first and second longitudinal edges; and an elastomeric element located between the upper and lower plates. The first and second laterally projecting flanges of the upper plate and lower plate are completely located above the vertical shoulders of the roller bearing adapter.

[0014] The first transverse edge of the upper plate and the second transverse edge of the upper plate may include curved sections in a top view, and the first transverse edge of the lower plate and the second transverse edge of the lower plate contain curved sections in a top view. The first transverse edge of the upper plate and the second transverse edge of the upper plate can also have a continuous radius in the plan view, measured from the vertical axis at the center point of the central portion of the upper plate, and the first transverse edge of the lower plate and the second transverse edge of the lower plate can also have a continuous radius of top view, measured from the vertical axis at the center point of the central portion of the bottom plate.

[0015] The first transverse edge of the upper plate and the second transverse edge of the upper plate form a side inwardly curved or angled inwardly from the outer surface of the upper plate to the inner surface of the upper plate in a side view, and the first transverse edge of the lower plate and the second transverse edge of the lower plate form bending inward or angled inwardly from the outer surface of the lower plate to the inner surface of the lower plate in side view.

[0016] The first longitudinal edge of the upper plate and the second longitudinal edge of the upper plate form a side bent inwardly or angled inwardly from the outer surface of the upper plate to the inner surface of the upper plate in a side view, and the first longitudinal edge of the lower plate and the second longitudinal edge of the lower plate form bending inward or angled inwardly from the outer surface of the lower plate to the inner surface of the lower plate in side view.

[0017] The elastomeric element may extend outward in the transverse direction beyond the first and second transverse edges of the upper and lower plates; and the elastomeric element may extend outwardly in the longitudinal direction beyond the first and second longitudinal edges of the upper and lower plates.

[0018] The highest strain values can occur in the direction inward of the outer edges of the elastomeric element when the upper plate is offset from the lower plate by 0.234 inches in the transverse direction. The upper plate, lower plate and elastomeric element of the adapter pad jointly provide a strain of less than 80% when the upper plate is offset by 0.234 inches in the transverse direction. The upper plate, lower plate and elastomeric element of the adapter cushion together provide a deformation of less than 90% when the upper plate is offset from the lower plate by 0.234 inches in the transverse direction.

[0019] The highest strain values occur in the direction inward of the outer edges of the elastomeric element when the upper plate is offset from the lower plate by 0.139 inches in the longitudinal direction. The upper plate, lower plate and elastomeric element of the adapter cushion together provide a strain of less than 80% when the upper plate is offset by 0.139 inches in the longitudinal direction from the bottom plate. The upper plate, lower plate and elastomeric element of the adapter pad together provide a strain of less than 90% when the upper plate is offset by 0.139 inches in the longitudinal direction.

[0020] The thickness of the sections of elastomeric elements located between the first and second transverse flanges of the upper and lower plates is pre-compressed relative to the static state.

[0021] The roller bearing adapter cushion system may also include a first compression pad located between the first transverse flange of the lower plate and the first vertical shoulder of the roller bearing adapter; and a second compression pad located between the second transverse flange of the lower plate and the second vertical shoulder of the roller bearing adapter.

[0022] The portion of the elastomeric member located between the central portions of the upper and lower plates may have a substantially uniform thickness.

[0023] In another example of the invention, there is provided a roller bearing adapter pad adapted for use with a three-piece trolley having AAR geometry, the adapter pad being adapted to interact with the axle box of the side frame. The adapter cushion may include a continuous upper plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upwardly directed portion, the first transverse flange having a first transverse edge, and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, wherein the continuous upper ina has first and second longitudinal edges; a continuous lower plate having a central portion, first and second upwardly extending portions protruding upward from opposing edges of the central portion, a first transverse flange protruding outward from the first upward directed portion, the first transverse flange having a first transverse edge, and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, the continuous lower plate having first and second longitudinal edges; and an elastomeric element located between the upper and lower plates. The first transverse edge of the upper plate and the second transverse edge of the upper plate form a side bent inwardly or angled inwardly from the outer surface of the upper plate to the inner surface of the upper plate in a side view, and the first transverse edge of the lower plate and the second transverse edge of the lower plate form a side directed at an angle inward from the outer surface of the bottom plate to the inner surface of the bottom plate in side view; and the first longitudinal edge of the upper plate and the second longitudinal edge of the upper plate form a side bend inwardly or angled inwardly from the outer surface of the upper plate to the inner surface of the upper plate in a side view, and the first longitudinal edge of the lower plate and the second longitudinal edge of the lower plate form or an edge directed at an angle inward from the outer surface of the lower plate to the inner surface of the lower plate in side view. The adapter cushion may also include a first compression pad located under the first transverse flange of the bottom plate; and a second compression pad located under the second transverse flange of the bottom plate.

[0024] The first transverse edge of the upper plate and the second transverse edge of the upper plate may include curved sections in a plan view, and the first transverse edge of the lower plate and the second transverse edge of the lower plate may include curved sections in a plan view.

[0025] The first transverse edge of the upper plate and the second transverse edge of the upper plate have a continuous radius in a plan view, measured from the vertical axis at the center point of the central portion of the upper plate, and the first transverse edge of the lower plate and the second transverse edge of the lower plate have a continuous radius in the form top, measured from the vertical axis at the center point of the central portion of the bottom plate. Any point on the transverse edge when the upper plate is rotated relative to the lower plate to 41 milliradians from the neutral position can have a linear offset less than or equal to 0.234 inches.

[0026] The elastomeric element can extend outward in the transverse direction beyond the first and second transverse edges of the upper and lower plates, and the elastomeric element extends outward in the longitudinal direction beyond the first and second longitudinal edges of the upper and lower plates.

[0027] The thickness of portions of elastomeric elements located between the first and second transverse flanges of the upper and lower plates can be pre-compressed relative to the static state.

[0028] An elastomeric member located between the central regions of the upper and lower plates may have a substantially uniform thickness.

[0029] The adapter pad may have a total longitudinal length of from about 6.5 inches to about 8.5 inches, and the adapter pad may have a total transverse length of from about 9 inches to about 11 inches.

[0030] The elastomeric element may have a Shore durometer hardness of 65 to 80 on a scale A.

[0031] In another example of the invention, there is provided a cushion system for a roller bearing adapter adapted to be used with a three-piece trolley having AAR geometry. The roller bearing adapter cushion system may include a roller bearing adapter adapted to interact with the roller bearing, the roller bearing adapter having an upper surface; and a lower surface adapted to interact with the roller bearing. The roller bearing adapter pillow system may also include an adapter pillow cooperating with the roller bearing adapter and configured to interact with the axle box of the side frame. The adapter cushion may include a top plate; bottom plate; and an elastomeric element located between the upper and lower plates. The upper plate, lower plate and elastomeric member together can provide a longitudinal stiffness of at least 45,000 pounds per inch, with a longitudinal displacement of the upper plate relative to the lower plate to 0.139 inches from a central position, a transverse stiffness of at least 45,000 pounds per inch, with a lateral displacement of the upper plate relative to the lower plate to 0.234 inches from the center position, and a rotational stiffness of at least 250,000 psi per radian of rotation, with rotationally displacing the top plate relative to the bottom plate up to 41 milliradians from a central position when exposed to a vertical load of 35,000 pounds on the central portions of the adapter pad. The roller bearing adapter may also include a first compression pad located under the first transverse flange of the bottom plate; and a second compression pad located under the second transverse flange of the bottom plate.

[0032] The highest strain values occur inward toward the outer edges of the elastomeric member when the upper plate is offset from the lower plate by 0.234 inches in the transverse direction. The upper plate, lower plate and elastomeric element of the adapter cushion together provide a deformation of less than 90% when the upper plate is offset from the lower plate by 0.234 inches in the transverse direction.

[0033] The highest strain values occur in the direction inward of the outer edges of the elastomeric member when the upper plate is offset by 0.139 inches in the longitudinal direction from the bottom plate. The upper plate, lower plate and elastomeric element of the adapter pad together provide a strain of less than 90% when the upper plate is offset by 0.139 inches in the longitudinal direction.

[0034] The portion of the elastomeric member located between the central portions of the upper and lower plates may have a substantially uniform thickness.

BRIEF DESCRIPTION OF THE DRAWINGS

[0035] Figure 1A is a perspective view of a standard three-piece trolley.

[0036] Figure 1B is an exploded view of a standard three-piece trolley.

[0037] Figure 2 is a perspective view of a roller bearing adapter and adapter pad in accordance with aspects of the present invention.

[0038] Figure 3 is a cross-sectional view of a roller bearing adapter, an adapter pillow, and a side frame in accordance with aspects of the present invention.

[0039] Figure 3A is a detailed view of the portion shown in FIG. 3.

[0040] Figure 3B is a detailed view of the portion shown in FIG. 3.

[0041] Figure 4 is a perspective view of a roller bearing adapter in accordance with aspects of the present invention.

[0042] Figures 5A-5D are general views of roller bearing adapters in accordance with aspects of the present invention.

[0043] FIG. 6 is a cross-sectional view of the roller bearing adapter shown in FIG. 4 taken along the center line.

[0044] FIG. 7 is a plan view of the roller bearing adapter shown in FIG. four.

[0045] FIG. 8 is a side view of the roller bearing adapter shown in FIG. four.

[0046] FIG. 9 is a front view of the roller bearing adapter shown in FIG. four.

[0047] Figure 10 is a sectional view taken along line A-A shown in FIG. 8.

[0048] Figure 11 is a plan view of an adapter pad in accordance with aspects of the present invention.

[0049] Figure 11A is a sectional view taken along line A-A shown in FIG. eleven.

[0050] Figure 11B is a sectional view taken along the line B-B shown in FIG. eleven.

[0051] FIG. 11C is a detailed view of a portion G shown in FIG. eleven.

[0052] Figure 12 is a side view of the bottom plate of an adapter pad in accordance with aspects of the present invention.

[0053] Figure 13A is a plan view of an adapter pad in accordance with aspects of the present invention.

[0054] FIG. 13B is a sectional view taken along the longitudinal line shown in FIG. 13A.

[0055] Figure 13C is a sectional view taken along a longitudinal center line of an adapter pad and a portion of a roller bearing adapter in accordance with aspects of the present invention.

[0056] Figure 13D is a perspective view of an adapter pad in accordance with aspects of the present invention, including a ground jumper, with elastomeric material removed.

[0057] Figure 13E is a perspective view of an adapter pad in accordance with aspects of the present invention including a ground jumper.

[0058] Figure 14 is an exemplary graph illustrating the relationship between lateral force and displacement for an adapter pad in accordance with aspects of the present invention.

[0059] Figure 15 is an exemplary graph illustrating the relationship between temperature and time under load of an adapter pad in accordance with aspects of the present invention.

[0060] Figure 16A is a plan view of an adapter pad in accordance with aspects of the present invention without a top plate.

[0061] Figure 16B is a cross-sectional view of an adapter pad in accordance with aspects of the present invention.

[0062] Figure 17A is a plan view of an adapter pad in accordance with aspects of the present invention.

[0063] FIG. 17B is a plan view of the adapter pad shown in FIG. 17A illustrating longitudinal displacement.

[0064] FIG. 17C is a plan view of the adapter pad shown in FIG. 17A illustrating lateral displacement.

[0065] FIG. 17D is a plan view of the adapter pad shown in FIG. 17A illustrating rotational displacement.

[0066] Figure 18 is an illustration of a method for manufacturing an adapter pad in accordance with aspects of the present invention.

[0067] Figure 19 is a perspective view of an elastomeric element of an adapter pad in accordance with aspects of the present invention.

[0068] Figures 20A-C are perspective views of a portion of an adapter pad in accordance with aspects of the present invention, illustrating various geometries for a plurality of gaps, wherein the adapter pad has an unloaded configuration.

[0069] Figures 21A-C are views of the corresponding Figures 20A-20C, schematically illustrating the geometry of the gaps, changed when the load on the adapter cushion.

[0070] Figure 22 is a cross-sectional view of a portion of an adapter pad in accordance with aspects of the present invention, illustrating a typical alignment of a plurality of gaps in an elastomeric portion.

[0071] Figure 23 is a cross-sectional view of a portion of an adapter pad in accordance with aspects of the present invention, illustrating a plurality of gaps extending only at a partial thickness of the elastomeric layer.

[0072] Figure 24 is an illustration of a method for manufacturing an adapter pad in accordance with aspects of the present invention.

[0073] Figure 25 is an illustration of a method for manufacturing an adapter pad in accordance with aspects of the present invention.

[0074] Figures 25A-25I are general views of adapter pads in accordance with aspects of the present invention.

[0075] Figure 26 is an illustration of a method of manufacturing an adapter pad in accordance with aspects of the present invention.

[0076] Figure 27 is an exemplary graph illustrating an adapter cushion test in accordance with aspects of the present invention.

[0077] Figure 28 is a perspective view of an adapter pad in accordance with aspects of the present invention.

[0078] FIG. 29A is a top view of the adapter pad shown in FIG. 28.

[0079] FIG. 29B is a plan view of the adapter pad shown in FIG. 28 illustrating plates in dashed lines.

[0080] FIG. 30 is a sectional view taken along line A-A shown in FIG. 29.

[0081] FIG. 31 is a detailed view of a portion of FIG. thirty.

[0082] FIG. 31A is a detailed view of another embodiment of a portion of an adapter pad similar to FIG. 31.

[0083] FIG. 31B is a detailed view of another embodiment of a portion of an adapter pad similar to FIG. 31.

[0084] FIG. 32 is a sectional view taken along the line B-B shown in FIG. thirty.

[0085] FIG. 33 is a detailed view of a portion of FIG. 32.

[0086] Figure 33A is a detailed view of another embodiment of a portion of an adapter pad similar to FIG. 33.

[0087] Figure 33B is a detailed view of another embodiment of a portion of an adapter pad similar to FIG. 33.

[0088] Figure 34A is a screenshot of a finite element analysis simulation result from a computer, illustrating deformation in the elastomeric region when the upper plate is offset in the transverse direction in accordance with aspects of the present invention.

[0089] Figure 34B is a screenshot of a portion of the results of a finite element analysis simulation shown in FIG. 34A.

[0090] Figure 35A is a screenshot of a finite element analysis simulation result from a computer, illustrating deformation in the elastomeric region when the upper plate is offset in the longitudinal direction from the lower plate in accordance with aspects of the present invention.

[0091] FIG. 35B is a screenshot of a portion of the results of a finite element analysis simulation shown in FIG. 35A.

[0092] Figure 36A is a perspective view of an adapter pad and a roller bearing adapter in accordance with aspects of the present invention.

[0093] Figure 36B is a side view of an adapter pad and a roller bearing adapter in accordance with aspects of the present invention.

[0094] Figure 36C is a top view of the adapter cushion and roller bearing adapter shown in FIG. 36A.

[0095] Figure 36D is a cross-sectional view of the adapter cushion and roller bearing adapter shown in FIG. 36C taken along line A-A.

[0096] Figure 36E is a front view of the adapter cushion and roller bearing adapter shown in FIG. 36A.

[0097] Figure 37 is a perspective view of an adapter pad in accordance with aspects of the present invention.

[0098] FIG. 38 is a plan view of the adapter pad shown in FIG. 37.

[0099] FIG. 39 is a bottom view of the adapter pad shown in FIG. 37.

[00100] FIG. 40 is a front view of the adapter pad shown in FIG. 37.

[00101] FIG. 41 is a rear view of the adapter pad shown in FIG. 37.

[00102] FIG. 42 is a side view of the adapter pad shown in FIG. 37.

[00103] FIG. 43 is a side view of the adapter pad shown in FIG. 37.

[00104] Figure 44 is a perspective view of an adapter in accordance with aspects of the present invention.

[00105] FIG. 45 is a front view of the adapter shown in FIG. 44.

[00106] FIG. 46 is a side view of the adapter shown in FIG. 44.

[00107] FIG. 47 is a rear view of the adapter shown in FIG. 44.

[00108] FIG. 48 is a side view of the adapter shown in FIG. 44.

[00109] FIG. 49 is a top view of the adapter shown in FIG. 44.

[00110] FIG. 50 is a bottom view of the adapter shown in FIG. 44.

DESCRIPTION OF THE PREFERRED EMBODIMENTS OF THE INVENTION

[00111] In the following description of various exemplary structures in accordance with the invention, reference is made to the accompanying drawings, which form a part thereof, and in which various exemplary devices, systems, and environments in which aspects of the invention may be practiced are shown. It should be understood that other specific constructions of parts, exemplary devices, media systems can be used, and that structural and functional modifications can be made without deviating from the scope of protection of the present invention. Also, although the expressions “upper”, “lower”, “front”, “reverse”, “lateral”, “rear”, and the like can be used to describe various exemplary elements and features of the invention, these expressions are used to convenience, for example, based on the exemplary orientations shown in Fig., or orientation in normal use. In addition, the expression "plural" in this context indicates any quantity greater than one, either conjunctively or disjunctively, if necessary, to an infinite number. Nothing in the present description should be construed as requiring a specific three-dimensional orientation of the structures to fall within the protection scope of the present invention. Also, the reader should understand that the attached drawings are not necessarily shown to scale.

[00112] Generally, aspects of the present invention relate to a railcar carriage and roller bearing adapters and pillow adapters of a railcar carriage. In accordance with various aspects and embodiments, a railcar carriage and roller bearing adapters and adapter carriage pillows of a railcar carriage can be made of one or more of a variety of materials, for example, metals (including metal alloys), polymers and composite materials, and can be made in one of many configurations without deviating from the scope of protection of the invention. It should be understood that the adapters of roller bearings and pillows of adapters of the carts of a railway carriage may contain components made of several different materials. In addition, components can be formed in various ways. For example, metal components can be formed by forging, molding, casting, stamping, machining and / or other known technologies. In addition, polymer components, for example, elastomers, can be manufactured using polymer processing technologies, for example, various molding and casting technologies and / or other known technologies.

[00113] The various figures in this application illustrate examples of railroad carriages, adapters of roller bearings of railroad carriages, and adapter pillows in accordance with the present invention. When the same reference position appears in more than one drawing, this reference position is used in the present description in a similar manner, and the drawings refer to the same or similar parts.

[00114] As shown in FIG. 1A and 1B, a typical rail freight wagon carriage includes an assembly consisting of two wheelsets 1, each of which includes two wheels 2, two side frames 4, one spring bar 6, two spring sets 8, a friction damping system, and four adapters 10. Figures 1A and 1B illustrate an exemplary trolley assembly.

[00115] The side frames 4 are arranged longitudinally, for example, in the direction of the rails along which the trolley moves. The nadressornoj beam 6 is aligned laterally or laterally with respect to the side frames 4 and passes through the middle of each side frame 4.

[00116] The thrust bearing 12 of the thrust beam is a circular portion of the thrust beam 6, which includes an upwardly projecting rim. The heel of the car body rests on the thrust bearing 12 of the nadressornoj beam and serves as a pivot point for the trolley and car body. At this border, the freight car exerts most of the vertical load. Typically, the thrust bearing 12 of the nadressor beam is equipped with wear-resistant plates or a wear-resistant liner, so that the casting 6 of the nadressor beam is not worn during the service life of the freight car. Also on the upper surface of the nadressornoj beam 6 and at a distance of 25 inches from the center line are the side bearings 14, which can help stabilize the car body and can to some extent prevent the wagons from wobbling, if they are of the type with constant contact. The side bearings 14 shown in FIG. 1B, do not belong to the type with constant contact, but consist of rollers and a separator.

[00117] The sprung beam 6 rests on the upper part of the spring sets 8, which are supported under the saddle of the spring of the side frames. Additional springs, often called damping or side springs 17, can also be part of the spring kit and rely on the spring seat extending up to the bottom of the friction wedges 16, which can be part of the friction damping system.

[00118] Friction wedges 16 may be located in pockets at the end and on each side of the nadressor beam 6. Pockets for frictional wedges of the nadressor beam can be located at an angle, usually at an angle of about 60 ° from the horizontal, corresponding to the angular surface of the friction wedges. The opposite surface of the friction wedge 16 is usually vertical and is in contact with the so-called column surface of the side frame. The elastic force of the damping springs 17 pushes the friction wedge 16 towards the angled surface of the pocket for the friction wedge of the overpressure beam, which creates a counteracting force relative to the vertical surface of the column of the side frame.

[00119] When the nadressornoj beam 6 is moved up and down under the load of a freight car resting on a trolley, sliding the friction wedge 16 over the surface of the column can create frictional damping of the column. This damping can provide energy dissipation, which prevents the occurrence of unwanted vibrations / vibrations of a freight car when traveling by rail. This also creates the forces acting between the nadressornoj beam 6 and the side frame 4 through the friction wedges 16, which prevents the deformation of the cart in the form of a parallelogram during operation. Rigid stops, such as ribs and rotation stops, help prevent deformation of the parallelogram cart. This resistance to deformation in the form of a parallelogram is often called skew stiffness.

[00120] As shown in FIG. 1A and 1B, the wheelset 1 of the trolley assembly consists of two wheels 2, an axle 3 and two roller bearings 5. The wheels are seated on the protruding access parts of the axle. Axle trunnions extend beyond the wheels and provide a mounting surface for roller bearings 5. Roller bearings 5 are mounted on axial trunnions. The boundary between the roller bearings 5 and the side frames 4 may consist of an adapter 7 of the bearing. Typically, railroad freight wagon trolleys are equipped with metal adapters that are machined with high precision to fit snugly enough on roller bearings and provide a looser fit on steel axle box openings of the side frames that bend around the boundary between the roller bearings and side frames. This boundary provides a slight movement between the wheelsets and the side frames, which is regulated by the vertical load from the freight car and the frictional forces between the sliding metal surface on the upper part of the adapter, called the convex surface of the adapter, and the lower part of the steel axle box, which is usually equipped with a steel wear plate.

[00121] Since the vertical load depends on the weight of the cargo contained in the freight car and on the swinging movement of the freight car on the trolley, in a conventional car, the frictional forces on the metal convex surface of the adapter and the steel wear plate of the axle box can vary significantly and are not under control. This metal-to-metal compound requires large wheel pair efforts to induce sliding on the boundary surface due to the intermittent sliding nature of the sliding metal compounds. Newer trolley designs, such as trolleys certified to the American Railways Association (“AAR”) specification M-976, include an adapter pad at the border between the steel adapter and the axle box.

[00122] Some adapter pillow systems have been able to reduce wheel pair forces when the wagon passes curves by providing low stiffness between the side frame and the axle. This additional flexibility created by the adapter cushion also reduces the force required to pull or push the wagon along a curve as required by specification M-976, which is incorporated herein by reference. On the other hand, these structures reduced the speed at which the car resonates during tangential movement along the tracks, in other words, they reduced the wagging speed of the cars. Reducing the wagging speed is a disadvantage, since it limits the operating speeds of trains and increases the risk of rail cars getting off the rail or damaging tracks. Other designs use additional devices to straighten the side frames, for example, cross beams, interframe mounts, pivot arms, spring supports, dampers, lateral mounts, or additional friction wedges to improve wobble performance. These systems, generally referred to as complementary trolley technologies, usually increase the wheel pair forces and, therefore, the traction resistance when passing curves. In addition to increasing drag when traversing curves, these designs typically increase the maintenance costs of the trolley due to additional wear components and system complexity.

[00123] Embodiments of an adapter pad system described herein may meet the performance criteria for traversing the curves set forth in M-976 without decreasing the critical wobble threshold. The adapter cushion systems described in this document also do not require the addition of any additional devices for straightening the side frames, such as the crossbeams, the interframe mount, the swing arms, the spring supports, the vibration dampers, the lateral mount or additional friction wedges, to the standard three-piece trolley. The resulting trolley system described herein can increase the life of the wheelset, maintain a high wobbling threshold, improve the durability of the cushion system and minimize wear and stress on the rails.

[00124] As prerequisites, there are many different types and types of wagons characteristic of the North American railway industry, which require different sizes of trolleys. 70 ton cars have a total car weight of 220,000 pounds and typically use 28-inch or 33-inch wheels with 6-inch by 11-inch bearings. 100 ton cars have a total car weight of 263,000 pounds and typically use 36-inch wheels with 6.5-inch by 12-inch bearings. The 110 ton carriages have a total car weight of 286,000 pounds and must comply with the M-976 performance specification, as noted above. These 110-ton rail cars typically use 36-inch wheels with 6.5-inch by 9-inch bearings. The latter type of wagon, typical of North America, is designed for 125 tons and has a total wagon weight of 315,000 pounds. This type of carriage typically uses 38-inch wheels with 7 inches by 12 inches bearings. Carts of other sizes (70 tons, 100 tons and 125 tons) do not fall under such a strict standard of performance and, therefore, today do not require the use of pillows.

[00125] The present application focuses on a roller bearing adapter and a corresponding adapter pad. Embodiments of the disclosed adapter system and the corresponding adapter cushion can be used in cars designed for 110 tons, and can be adapted to use and improve the performance of carts for cars of all carrying capacities (including 70 tons, 100 tons, 110 tons and 125 tons ), including trolleys that do not require compliance with the M-976 standard.

[00126] One embodiment of an adapter pad system 198 is shown in at least FIG. 2 and 3. The adapter pillow system 198 may include a roller bearing adapter 199 and an adapter pillow 200 adapted to fit between a roller bearing of a pair of wheels or a roller bearing 5 and an axle box 152 of a side frame of a three-element truck of a railway carriage. The side frame may include first and second outer sides 154, 156. The adapter pad 200 also includes an elastomeric element 360 that supports vertical loading and provides slight longitudinal, lateral and rotational movement of the upper plate 220 (interacting with the side frame) relative to the lower plates 240 (interacting with a roller bearing adapter) compared to a traditional steel-to-steel sliding adapter system.

[00127] In some embodiments, as shown in at least FIG. 2-3, the adapter cushion system 198, when installed in a trolley system, is compressed with a constant vertical load due to the weight of the wagon and trolley components that are held by the adapter cushion 200 and are ultimately carried along the wheelset. Although the vertical load transmitted to the central portion of the adapter pad 200 naturally varies with different wagon loads, it is estimated that the vertical load may be about 35,000 pounds per adapter pad for a corresponding gross vehicle weight of about 286,000 pounds.

[00128] During the tests, it was determined that the rigidity of the adapter pad 200 greatly affects the performance of the trolley system. In particular, in some embodiments, it is determined that the performance of the trolley can be improved by using the improved performance of the adapter pad system. The performance of the adapter pad system can be improved by increasing the rigidity of the adapter pad system 198 (measured in pounds of force per inch bias). In addition, for example, it is determined that an acceptable life expectancy (measured in the distance covered by the load of the trolley system, which includes an installed adapter cushion 200, the service life of which is 1 million miles of carriage travel), adapter cushions 200, such as in embodiments herein, it is expected that the longitudinal stiffness is at least 45,000 pounds per inch or is in the range of from about 45,000 pounds per inch to about 80,000 pounds per inch, and / or when the transverse stiffness is at least 45,000 pounds per inch or is in the range from about 45,000 pounds per inch to about 80,000 pounds per inch, and / or when the rotational stiffness (i.e., the stiffness for resistance to rotation around the vertical axis) is at least 250,000 pounds per inch per radian, or in the range of about 250,000 pounds per inch per radian to about 840,000 pounds per inch per radian (each measured by a vertical load of 35,000 pounds on the central portion adapter 200). These unique stiffness combinations can maximize the threshold wobble speed while still maintaining curve resistance below 0.40 lb / ton / degree of curvature as required by specification M-976, without the use of additional trolley technologies such as crossbeams, frame mount, swing arms, spring mounts, dampers, lateral mounts, or additional friction wedges to improve performance.

[00129] The rigidity of the adapter pillow system is quantified by measuring the resistance of the adapter assembly to the relative shear displacement of the upper plate (which interacts with the side frame) and the lower plate (which interacts with the roller bearing adapter). To determine the stiffness, the adapter assembly can be offset relative to the side frame in many directions, for example, in the longitudinal direction (in the direction of the carriage), the transverse direction (across the rail tracks), the yaw direction (rotation around the vertical axis and in line with the axial center line ) and the vertical direction (between the axle box of the side frame and the upper surface of the adapter cushion). To simulate a loaded wagon scenario during a shear stiffness test, a vertical load of 35,000 pounds should be supported.

[00130] During the test, the force to bias the upper plate relative to the lower plate can be measured using load sensors attached to a power actuator. Displacement measurements can be obtained using displacement transducers, dial gauges, potentiometers, or other instruments for measuring displacement. As described in more detail below, the force and displacement are plotted, with the slope of the hysteresis loop indicating stiffness in the corresponding direction. The area inside the loop is proportional to the energy transferred during load cycling.

[00131] Embodiments of an adapter pad system 198 described herein provide a hole width and a spacing therebetween that is sufficient to not limit displacement within AAR values, even when using high rigidity slide pillows, as described herein. The disclosed adapter design may use the target adapter offsets shown in Table 1 below.

Table 1

NEW COMPONENTS WITH A GAP BETWEEN THE ADAPTER AND LATERAL FRAME ACCORDING TO AAR STANDARD Signs Nominal Maximum Minimum Longitudinal clearance
(Each direction from the center: inches) 0,047 0.139 0.017 Lateral clearance
(Each direction from the center: inches) 0.156 0.234 0,126 Rotational clearance
(Each direction from the center: mrad) 26.1 41.0 9.2

[00132] The disclosed embodiments of a longitudinally, transverse, and rotationally reinforced adapter pad system 198, as described herein, can provide a preferred combination of stability at high speeds and low drag when running curves for a three-piece trolley system. The disclosed embodiments of the adapter cushion system 198 can improve the bias control of the three-element trolley system compared to other adapter cushion designs. This can provide improved stability at high speeds. In addition to improving stability at high speeds, embodiments of the adapter cushion system 198 described herein can facilitate longitudinal displacement of the wheelset as the curves pass, allowing the front and rear axles of the trolley assembly to develop a center yaw angle proportional to the curve, which can reduce wheel forces steam Taken together, the adapter cushion system 198 promotes a lateral shift of the wheel pairs to develop the optimum difference in rolling radius during the passage of the curves. The stiffness and displacement ranges of the adapter pad system disclosed herein can provide optimal center yaw angle and lateral displacement of the wheel pairs, helping to reduce wheel pair forces during the passage of the curves. Reduced stress in traversing curves and improved stability at high speeds can help increase the life of wheelsets and rails.

[00133] In some constructions of the adapter pad, a plurality of elastomeric layers are used to reduce shear strain. Many layers can add significant thickness to the adapter system and, when used in traditional carts, increase the height of the wagon. Increasing the height of the car creates problems when coupling with other cars, and also raises the center of gravity. As a result, some designs require the use of special, unconventional side frames to minimize height differences. The embodiments described herein can provide improved dynamic performance without the need for special, unconventional trolley components.

[00134] The embodiments described herein can be used with side frames having AAR geometry, including AAR axle box geometry and AAR gaps between abutment protrusions, as described in the American Association of Standards and Recommended Practices Railways, section Sll (10/25/2010), specification S-325 (6/11/2009) entitled “Side Frame, Narrow Pedestal - Limiting Dimensions”, which is incorporated herein by reference. The geometry of the AAR axle box opening can be described as including a nominal longitudinal distance between the abutment protrusions of about 7.25 to about 8.25 inches; a nominal width of the thrust protrusion of from about 3.5 to about 3.75 inches; a nominal longitudinal distance between the jaws of about 8.88 to about 11.06 inches; and the nominal height of the axle box above the centerline of the axis, comprising from about 5.38 to about 6.89 inches. Embodiments of an adapter pad system 198 disclosed herein may be used with existing and / or standard three-piece cart systems, including cart systems having AAR geometry as described in the American Railroads Association of Standards and Recommended Practices and, in in particular, in section H (1/1/2012), specification M-924 (2/1/2014) entitled “Journal Roller Bearing Adapters for Freight Cars”, which is incorporated herein by reference. The gap between the abutment protrusions according to the AAR standard can be found in Table 1 above for new production casting sizes. The gap between the thrust protrusions is determined through the distance between the axle box and the holes of the roller bearing adapter. AAR adapter sizes may include a nominal longitudinal distance between the abutment surfaces of the abutment protrusions of about 7.156 to about 8.656 inches; and a nominal lateral bore of the thrust protrusion of from about 3.812 to about 4.062 inches. Embodiments of adapter pillow system 198 described herein may also be in accordance with American Railroad Association ("AAR)" M-976 (AAR Standards and Recommended Practices, Section D (9/1/2010), M-976 ( 12/19/2013) called "Truck Performance for Rail Cars"), which is incorporated herein by reference. For example, embodiments of an adapter pad system 198 may be used in existing and / or standard three-piece cart systems without the use of additional elements such as crossbeams, frame mounts, or spring supports. Furthermore, for example, the adapter pad systems 198 disclosed herein may be mounted between the roller bearing 5 and the axle box 152 of existing carts. Thus, the adapter pad system 198 disclosed herein may have a total height, measured between the upper surface of the roller bearing 5 and the axle box 152, of about 1.3 inches or in the range of about 1.1 inches to about 1, 5 inches Although the embodiments described herein relate to a 110-ton truck, the disclosed adapter system and associated adapter pad can be adapted to use and improve the performance of carts for wagons of all carrying capacities (70 tons, 100 tons, 110 tons and 125 tons) including trolleys that do not require compliance with the M-976 standard.

[00135] A roller bearing adapter 199 in accordance with the present invention is shown in FIG. 4-10. As shown in FIG. 4, the roller bearing adapter 199 includes a axial convex surface 102. In some embodiments, the axial convex surface or the upper surface 102 may be a convex or curved surface such that a central portion of the axial convex surface is higher than the transverse edges. Thus, the axial convex surface 102 may be generally flat in the longitudinal direction and curved in the transverse direction. The articulated convex surface 102 may be an AAR articulated convex surface, but may have a smaller sectional thickness than a typical roller bearing adapter. For example, in some embodiments, the thickness of the roller bearing adapter can range from about 0.6 inches (measured from the bearing surface 117 to the axial axle plate 102) to about 0.75 inches and in some embodiments less than about 0.75 inches.

[00136] As shown in FIG. 4-8, the roller bearing adapter 199 may have a total height of from about 4.83 inches or in the range of from about 4 inches to about 6 inches; a total length of about 9.97 inches or in the range of about 9 inches to about 11 inches; and a total width of about 10 inches, or at least 7.5 inches, or in the range of about 9 inches to about 11 inches.

[00137] The roller bearing adapter 199 may include elements for restricting the movement of the adapter pad 200 relative to the roller bearing adapter 199. For example, a roller bearing adapter may include longitudinal adapter pillow guides 104. As shown in FIG. 4, the longitudinal cushion stops 104 can vertically protrude relative to the transverse edges of the axle box convex surface 102. The longitudinal cushions of the adapter cushion 104 are configured to interact with the grooves, recesses, or the edges of the bottom plate 240 of the adapter cushion 200 and can interact with the adapter cushion 200, so that the longitudinal movement adapter pad 200 may be limited or adjusted to a certain value, without limiting the lateral movement of the adapter pad. Although in FIG. 4 shows four longitudinal adapter cushion stoppers 104, any number or any design of longitudinal cushion stops can be used, including continuous longitudinal cushion stops that extend along the entire length of the transverse edge of the axle plate convex surface 102. Examples of other possible longitudinal limiters 104 are shown in FIG. 5A-5D. For example, the longitudinal stops 104 may include two protrusions on the transverse sides, as shown in FIG. 5A. The longitudinal stops 104 shown in FIG. 5A can interact with relief elements in the bottom plate 240 of the adapter pad 200, which can engage these stops 104, so that longitudinal movement can be limited. Like FIG. 5A, in FIG. 5B shows three stops 104 that can limit the longitudinal movement of the adapter pad 200 with respect to the adapter 199 in a similar manner.

[00138] Longitudinal stops may be integrated into other portions of the adapter pad. For example, as shown in FIG. 5C and 5D, the longitudinal stops 104 can be embedded in the upper surface of the vertical shoulder 106. Similarly, in these examples, the relief elements in the bottom plate 240 of the adapter pad can cover these stops 104 or protrusions and limit the longitudinal movement of the bottom plate 240 relative to the upper plate 220 .

[00139] For the longitudinal stops 140, various other combinations of sizes, shapes, and locations may be used to provide the desired travel restriction.

[00140] As shown in FIG. 4-8, the roller bearing adapter 199 also includes vertical shoulders 106. The vertical shoulders 106 may vertically protrude relative to the longitudinal edges of the axial convex surface 102. The vertical shoulders 106 are configured to improve the flexural strength of the adapter 199 and minimize the bending of the adapter 199 when exposed to large efforts from a pillow 200 adapter. By minimizing the curvature of the adapter pad 200 under load, the vertical shoulders 106 can improve the load distribution on the components of the roller bearing and can increase the bearing life. The vertical shoulders 106 are adapted to interact with the grooves, recesses, edges or surfaces of the lower plate 240 of the adapter pad 200, so that the lateral movement of the lower plate 240 is limited or adjusted to a certain value. In addition to restricting the movement of the bottom plate, in some embodiments, the vertical shoulders can provide vertical support for the transverse flanges 116, 118 of the adapter pad 200. Vertical shoulders 106 may extend laterally 10 inches wide for a 6.5 inch by 9 inch adapter and vertically about 1 inch above a standard axial convex surface. In some embodiments, the upper surface of the vertical shoulders 106 may protrude up to about 0.75 inches or up to about 3 inches above the axial convex surface 102. The vertical shoulders can also extend up to about 8 inches in the longitudinal direction. Vertical shoulders can be molded in one piece with an adapter and are used on standard adapters for 70 tons, 100 tons, 110 tons or 125 tons. Although continuous vertical shoulders are shown, any number of vertical shoulders can be used. The width of the vertical shoulders may be at least 0.5 inches.

[00141] The roller bearing adapter 199 may also include elements, for example, vertical shoulders 106, to improve the bending strength or inertia of the cross section of the adapter 199 to minimize distortion of the adapter 199 when exposed to high forces from the adapter pad 200. For example, for the embodiment shown in FIG. 4 and 6-10 and, in particular, shown in FIG. 8 and 10, the cross section of the adapter 199 can be taken approximately through the longitudinal center of the roller bearing adapter 199, as shown in FIG. 8 and 10. As shown in FIG. 10, the neutral Y-axis 108 can extend vertically through the transverse center of the adapter 199. The neutral Z-axis 110 can extend laterally about 5.2 inches or in the range of about 5.0 inches to 5.5 inches above the center axis axis 111. The moment of inertia of the section shown in FIG. 10, around the neutral Z-axis 110, I zz, in the center of the adapter may be about 1.4 inches ^4, or in the range of about 1.0 to about 2.0 inches ⁴ . The moment of inertia of the cross section around the neutral Y-axis 108 in the center of the adapter, I yy, can be about 86.8 inches ⁴ or in the range from about 50 to about 100 inches ⁴ . Designs of adapters that do not use vertical shoulders have a significantly lower moment of inertia in sections. For example, the adapter design shown in FIG. 10, but without vertical shoulders 106 with the same cross section along the transverse center line, may have an inertia moment around the neutral Z axis of about 0.2 inches ⁴ and may have an inertia moment around the neutral Y axis of about 32.9 inches ⁴ . The resulting lower moment of inertia compared to the disclosed adapter may result in lower stiffness and higher stresses in the adapter under the same load configurations and, possibly, to a deterioration in the performance of the roller bearing.

[00142] The roller bearing adapter 199 may be made of one or more different types of steel alloys that have suitable strength and other characteristics. For example, a roller bearing adapter 199 may be made of cast iron ASTM A-220, A-536 or cast or forged steel ASTM A-148, A-126 A-236 or A-201. In some embodiments, the entire roller bearing adapter 199 is made (by casting, machining, pressing, or other suitable metal forming operation) of one monolithic element.

[00143] Next, we will turn to the adapter pad 200 of the adapter system 198, which is adapted to be placed between the roller bearing adapter 199 and the axle box 152 of the side frame 4 and can interact with them. As shown in FIG. 11-11C, and mainly in FIG. 11A, adapter pad 200 generally includes an upper element or upper plate 220 having an inner surface 222 and an outer surface 224, a lower element or lower plate 240 having an inner surface 242 and an outer surface 244, and an elastomeric element 360 located between the inner surfaces 222, 242 of the upper and lower plates 220, 240 along the portion of the pad 200 of the adapter. The adapter cushion 200 includes a central portion 210, which is located under the lower surface of the axle box 152, with each plate 220, 240 having a corresponding central portion 226, 246. The adapter cushion 200 further includes first and second upwardly extending portions 212, 214 and first and second transverse flanges 216, 218. The upper plate 220 has respective first and second upwardly directed portions 228, 230 protruding upward from opposite edges of the central portion 226 of the upper plate 220, the first transverse a flange 232 protruding outward from the first upwardly extending portion and a second transverse flange 234 protruding outwardly from the second upwardly extending portion 230. Similarly, the lower plate 240 has respective first and second upwardly extending portions 248, 250 protruding upward from the opposite edges of the central section 246 of the lower plate 240, a first transverse flange 252 protruding outward from the first upwardly directed portion, and a second transverse flange 254 protruding outwardly from the second upwardly directed portion 250. As Zano FIG. 3, in the assembled state of the trolley system, the transverse flanges 216, 218 extend laterally beyond the axle box 152, and the central portion 210 is located under the axle box 152. The first and second upward sections 212, 214 are located between the central section 210 and the corresponding first and second transverse flanges 216, 218 and provide a transition between them.

[00144] First, reference is made to the central portion 210, which in some embodiments may comprise mainly three parts, including the central portion 226 of the upper plate, the central portion 246 of the lower plate, and the elastomeric member 360 located between them. As discussed above, an adapter pad 200 is located between the axle box 152 of the side frame, which generally has a substantially flat horizontal contact surface, and the roller bearing adapter 199, which may generally have a curved or convex arch. As shown in FIG. 11A and 12, the central portion 246 of the lower plate 240 may have a curved lower surface 244 so that the outer surface 244 generally repeats the bending or convexity of the adapter 199. In particular, in some embodiments, the central portion 246 may have a greater thickness towards the edges 261 262 of the central portion 246 than in the center of the central portion 246. For example, as shown in FIG. 12, the thickness at the center of the central portion 246 may be about 0.15 inches or in the range of about 0.06 inches to about 0.35 inches, and the thickness at the edges 261, 262 can be about 0.26 inches or in the range of about 0.15 inches to about 0.5 inches.

[00145] In some embodiments, the central portion 226 of the upper plate 220 may include an outer surface 224 and an inner surface 222 that are substantially horizontal and parallel, as shown in FIG. 11A. The thickness of the central portion 226 of the upper plate 220 may be about 0.28 inches or in the range of about 0.15 inches to about 0.4 inches. In such a system, the thickness of the elastomeric portion 360 may be substantially the same throughout the central portion 210, which in some embodiments may improve performance.

[00146] It has been found that an elastomeric portion having a uniform thickness may have some advantages in some cases. For example, in some embodiments, linear thermal shrinkage may be constant along the length and width of the cushion if the plurality of elastomeric layers has the same length and width across all elements. For example, in some embodiments, during molding, the rubber forming the elastomeric element can be introduced into the mold at about 300 degrees Fahrenheit, and then it can be cooled to room temperature. The linear thermal shrinkage normal to the shear plane may be related to the thickness “T” of the section, temperature change, and coefficient of thermal expansion. Uneven elastomer thickness can lead to uneven shrinkage during cooling. Uneven shrinkage can lead to residual tensile stresses in areas that are cooled last, which can adversely affect the fatigue life.

[00147] With further reference to FIG. 11-11C, and mainly in FIG. 11C, in some embodiments, the first and second upwardly directed portions 228, 230 of the upper plate 220 may include an outer flat portion 228a, 230a (only the first upward portion is shown in FIG. 11C) and an inner flat portion 228d, 230d. In some embodiments, planar sections 228a, 230a and 228d, 230d may extend at an angle Δ relative to a plane P that extends along the outer surface 224 of the central portion 226. In some embodiments, the angle Δ may be an obtuse angle, and in some embodiments, the angle can range from about 95 degrees to about 115 degrees, for example, 105 degrees or any other angle within this range. As described in more detail below, in embodiments in which the first and / or second upwardly extending portions 212, 214 include a hook, a flat surface may surround one or both sides of the hook or may alternatively be positioned relative to the hook. The first and second upwardly directed portions 228, 230 of the upper plate 220 may also include lower curved portions 228b, 230b and 228e, 230e, which are a transition between the central portion 226 and the flat portions 228a, 230a and 228d, 230d. Similarly, the first and second upwardly directed portions 228, 230 of the upper plate 220 may also include upper curved portions 228c, 230c and 228f, 230f, which are the transition between the transverse flanges 232, 234 and the flat portions 228a, 230a and 228d. 230d. The upper or lower curved sections 228b, 230b, 228e, 230e, 228c, 230c, 228f and 230f may be formed with constant curvature and / or variable curvature. The bottom plate 240 may include similar planar sections and upper and lower curved sections. In some embodiments, upwardly directed portions 212, 214 may not include a planar portion and may be formed with constant curvature and / or variable curvature.

[00148] With further reference to FIG. 11A, the first and second transverse flanges 216, 218 can extend laterally beyond the side frame 4 and are located at a vertical height or in a plane that is different or located above the central portion 210 located below and in contact with the axle box 152. Accordingly, the first and second transverse flanges 216, 218 are arranged in a vertically elevated position relative to the central portion 210. The transverse protruding flanges 216, 218 can provide a large area for the elastomer and, as discussed below, can increase the stiffness of the adapter cushion. In some embodiments, as shown in FIG. 13B, the outer surface 244 of the first and second transverse flanges 252, 254 of the bottom plate 240 may be about 0.92 inches higher than the outer surface 244 of the lower edge of the bottom plate 240 or in the range of about 0.25 inches to about 2 inches. In some embodiments, the first and second transverse flanges 216, 218 may include flat and horizontal outer surfaces 224, 244, which may be parallel to the outer surface 244 of the central portion 226. In some embodiments, the outer surface 244 of the first and second transverse flanges 252 254 of the lower plate 240 may rest on the vertical shoulders 106 of the roller bearing adapter 199. In other embodiments, the outer surface 244 of the first and second transverse flanges 252, 254 of the lower plate 240 does not contact the vertical shoulders 106. In other embodiments, the outer surface 244 of the first and second transverse flanges 252, 254 of the lower plate 240 can indirectly contact the vertical shoulders 106 through another element, such as a compression pad. As will be discussed in more detail below, in some embodiments, from about 10 percent to about 30 percent of the vertical force from the axle box 152 can be distributed to each of the transverse flanges 216, 218 of the adapter pad when the vertical force is applied to the central portion 210 of the adapter pad.

[00149] Although an embodiment of an adapter pad 200 shown in at least FIG. 11-13, includes upwardly directed portions 212, 214 and transverse flanges 216, 218, these portions are optionally included in all embodiments. In some embodiments, the central portion 210 may be used without transverse flanges 216, 218 and / or without upwardly extending portions 212, 214, although such designs may affect performance. In an embodiment, the transverse flanges 216, 218 may extend from the central portion without upwardly extending portions and without compromising performance. Similarly, in some embodiments, the transverse flanges may extend beyond the central portion, but in the same plane as the central portion. In other embodiments, the adapter pad 200 may include downwardly directed portions that can be connected to the transverse flanges.

[00150] The upper plate 220 may be made of one or more different types of alloys with suitable strength and other characteristics. For example, the top plate 220 may be made of ASTM A36 steel plate or steel with strength equivalent to or greater than ASTM A-572. In some embodiments, the entire upper plate 220 is formed (by casting, machining, pressing, rolling, stamping, forging, or another suitable metal forming operation) from one monolithic element. In some embodiments, the top plate 220 may be made of a material with a constant thickness. In other embodiments, top plate 220 has a variable thickness. For example, in some embodiments, the transverse flanges 232, 236 of the upper plate 220 may have a thickness that is greater or less than the thickness of the central portion 226. Similarly, and as previously discussed, the lower plate 240 may have a constant or variable thickness. In some embodiments, one, several, or all of the corners 233 of the upper plate 220 may be rounded.

[00151] In some embodiments, the outer surface 226 of the upper plate 220 may be coated with an elastomeric material 265, which is a material that is in contact with the axle box 152. As discussed herein, the elastomeric layer 265 can provide damping and calibrated cushion flexibility, and also a compressible surface to minimize wear between the adapter pad 200 and the axle box 152. An elastomeric coating 265 can be formed with a flat outer surface that repeats the geo the metric profile of the steel portion of the upper plate 220, and may have a uniform thickness either throughout the entire upper plate 220, or in other embodiments, a uniform thickness within individual sections of the cushion, for example, a uniform thickness in the central portion 210, a uniform thickness (possibly different or possibly the same) on one or both transverse flanges 232, 234 of the upper sections, uniform thickness (possibly different or possibly the same) on one or both upward sections 228, 230, and the like.

[00152] When using the adapter 200 in the pillow 200, heat may be generated by friction of the pillow 200 and sliding relative to the axle box 152 of the side frame and / or relative to the bearing adapter 199; and / or hysteretic damping of the elastomeric member 360 of the adapter pad 200. These heat sources can cause an increase in the temperature of the adapter cushion, which can lead to a decrease in wear resistance and a decrease in stiffness.

[00153] In some embodiments, the first and second transverse flanges 216, 218 may include upper and lower surfaces exposed to air outside the envelope curve of the side frame in the axle box (when the adapter pad is installed within the axle of the carriage). Exposed surfaces can easily provide heat loss to the adapter cushion while the car is moving (acting as a rib) and can induce clean heat flow from the center portion 210 of the adapter cushion 200 toward the transverse flanges 216, 218. As will be understood, and as discussed below, heat stands out in the adapter cushion 200 during car operation for various reasons, for example, due to friction, which resists the relative movement or rotation between the adapter cushion 200 and the side frame and between Adapter pad 200 and the bearing adapter 199. In addition, since the adapter pad 200 is in surface contact with the side frame 4 and the bearing adapter 199, the adapter pad 200 can receive heat that is generated elsewhere and transferred to the adapter pad 200. Also, cyclic damping of the elastomeric section produces heat. This heat should ultimately be diverted to prevent a substantial increase in the temperature of the components of the adapter pad 200 in order to increase the life of the components, as well as to reduce possible design constraints that may be necessary if the adapter pad 200 (or portions of the adapter pad 200) are continuously operating at higher temperatures in the absence of heat dissipation. This heat flow from the adapter pad 200 can contribute to the thermal design of the adapter pad 200 and the rest of the trolley system, which can have various design advantages, for example, expanding the selection of possible elastomeric materials, as well as increasing the life of the elastomeric material by lowering its operating temperature as other possible benefits.

[00154] In some embodiments, the adapter pad 200 may include additional elements that can improve its ability to reduce heat in the adapter pad 200. For example, in some embodiments, the first and / or second transverse flanges 216, 218 may include a portion that extends laterally from the side walls of the axle box region of the side frame. In use, the transverse flanges are in direct contact with the air flow generated by the movement of the car, in contrast to the central portion, which is insulated with a metal roller bearing adapter and a steel axle box side frame. These transverse flanges may provide a free surface area for transferring heat to the atmosphere from the adapter pad 200. This can contribute to heat dissipation due to hysteretic cycling of the elastomer, increasing the temperature of the roller bearing and any other heat in the adapter pad 200. In some embodiments, with the first and / or second transverse flanges 216, 218, the operating temperature of the adapter pad system 198 can be reduced. For example, during normal cyclic shear operation, as described below, the temperature difference between the transverse flanges 216, 218 and the center of the pad when using air flow at a constant speed of 5 mph along the first and second transverse flanges 216, 218 can be about 15 degrees Fahrenheit or in the range of about 5 degrees Fahrenheit to about 25 degrees Fahrenheit. Improved heat transfer from the center of the pillow to the transverse flanges can provide an additional improvement in heat transfer to the atmosphere and, therefore, increased wear resistance.

[00155] In some embodiments, one or both of the outer surface 224 of the central portion 226 or the inner surface 244 of the central portion 246 may include one or more different surface elements and, in some embodiments, a pattern of surface elements in order to make these surfaces non-smooth. For example, the upper surface may include one or more bulges, protrusions and recesses, rough surfaces, “sticky” surfaces, and the like. These surfaces can be obtained in several ways, including bead blasting, mechanical surface treatment, applying various materials, for example, various types of rubber, to the surface, etc. If present, these surface elements can reduce the possibility of lateral and / or longitudinal sliding and / or relative rotation of the adapter cushion relative to the axle box 152, which can improve the dynamic load characteristics and strength of the adapter cushion 200, and can also reduce localized heat generation in the adapter cushion 200 due to friction between the adapter cushion 200 and the axle box 152, which must be removed from the adapter cushion 200 (as discussed herein). Similarly, a thermal barrier coating, such as ceramic or porcelain, can be applied to the upper or lower plates 220, 240. Optionally, for thermal insulation of heat generated as a result of frictional sliding at high amplitudes, a thermal barrier plate can be used. This can be done in conjunction with a wear resistant plate, which is commonly used with steel adapter plates. The plate may be formed so that an air gap is maintained and contact areas are located at the outer edges of the adapter.

[00156] The lower plate 240 may have a similar construction and be made of the same materials as the upper plate 220. Similarly, the outer surface 244 of the lower plate may include machined surfaces and coatings of elastomeric material 265, as well as the upper plate.

[00157] In some embodiments, all or most of the adapter pad 200 may include a coating of elastomeric material 265, as shown, for example, in FIG. 13C and FIG. 13E. In some embodiments, for example, a coating of elastomeric material may be in contact with axle box 152, side frame 4, and roller bearing adapter 199, including axle box surface 102 and vertical shoulders 106. In other embodiments, for example, portions of adapter pad 200, which in contact with the axle box 152, the side frame 4 and the adapter 199 of the roller bearing, may not be covered with elastomeric material. As discussed herein, elastomeric layer 265 can provide cushion damping and calibrated flexibility as well as a compressible surface to minimize wear between adapter cushion 200, axle box 152 and roller bearing adapter 199. The elastomeric coating 265 may repeat the shape of the outer surfaces of the adapter pad 200 and may have a uniform thickness along the outer surfaces of the adapter pad 200 or in other embodiments, uniform thickness within individual portions of the pad, for example, a uniform thickness on the central portion 210, a uniform thickness (possibly different or possibly the same) on one or both transverse flanges 232, 234, uniform thickness (possibly different or possibly the same) on one or both upward ah 228, 230, etc.

[00158] In some embodiments, it is possible to use an electrically conductive additive in the elastomeric materials discussed herein to provide electrical conductivity and shunt power to the upper and lower plates 220, 240. These additives can include materials, such as nickel-plated graphite, silver plated aluminum, or silver plated copper. To ensure sufficient electrical conductivity, the amount of these additives can be as little as 0.5% of the total elastomer volume. Similarly, a flexible conductor connecting the upper plate and the lower plate can be molded to create an electrical connection between the side frame of the trolley and the adapter in the elastomeric cushion. The conductor sheath can protect the conductor from atmospheric corrosion. Its flexibility allows it to bend when the elastomeric (e.g. rubber) material is deformed. In some embodiments, as shown in FIG. 13D-13E, electrical continuity between the side frame 4 and the adapter 199 is provided by using a ground wire jumper 266. As shown in FIG. 13D-13E, the ground wire jumper 266 can be attached to the upper and lower plates 220, 240 using holes 267 that can be located less than about 0.20 inches from the edge of the plate. The ground wire jumper 266 passes through holes 267 in the upper and lower plates 220, 240. The edges of the plates may have cutouts or recesses 268 for crimping or securing the wire ground jumper 266. In some embodiments, the wire ground jumper 266 may be a stainless steel braid with a diameter about 0.100 inches, but may have a diameter of just 0.050 inches.

[00159] In some embodiments, as shown in FIG. 11, the adapter pad 200 is configured to be symmetrical about a transverse vertical plane that passes through the geometric center C of the adapter pad (shown as the passage line B in FIG. 11), and / or is symmetrical about a longitudinal vertical plane that extends through the geometrical center C of the adapter pad 200 (shown as a passage line A in FIG. 11).

[00160] In some embodiments, each of the outer transverse edges 281, 282 of the transverse flanges of the upper and lower plates 220, 240 is aligned along the same vertical plane, as best shown in FIG. 11C. In these embodiments, the transverse length of the transverse flange of the lower plate 240 is less than the transverse length of the transverse flange of the upper plate 220.

[00161] Exemplary dimensions of an adapter pad 200 are shown and described herein; however, other dimensions may be used for the adapter pad sections, depending on the fixed dimensions of the side frame and bearings used with the particular rail carriage system.

[00162] In some embodiments, as shown, for example, in FIG. 3 and 11-11C, the adapter pillow 200 may also include pillows or hooks on the upper and lower plates of the adapter pillow 220, 240, which may be configured to position the adapter pillow 200 relative to the axle box 152 of the side frame and bearing adapter 199, and also interactions and restrictions on the movement of the adapter pad 200 relative to the axle box 152 and the bearing adapter 199, which can focus the movement (ie, shift) of the adapter pad 200 on the elastomeric member 360. Connection of the pillows and 200, the adapter with the roller bearing adapter 199 may cause the centering of the adapter pad 200 to be centered relative to the roller bearing and bearing adapter 199 by using the vertical shoulders 106 and engaging the hooks. In addition, the adapter pad system 198 facilitates the return of the adapter 199 and the wheelset to a centered or central position with close to zero force.

[00163] For example, adapter pad 200 may include a first transverse adapter hook 270 located between first vertical shoulder 106 of adapter 199 and first upward portion 248 of bottom plate 240; and a second transverse adapter hook 271 located between the second vertical shoulder 106 of the adapter 199 and the second upward portion 250 of the bottom plate 240. The transverse hooks 270, 271 of the adapter may extend along the entire longitudinal length of the adapter pad 200 or along the longitudinal length of the adapter pad 200. In other embodiments, the transverse hooks 270, 271 may comprise a plurality of transverse adapter hooks that extend along the entire transverse length of the adapter pad 200 or at any portion thereof.

[00164] The transverse hooks 270, 271 of the adapter pad can be integral with the bottom plate 240, including integrally with any elastomeric coating 265 on the adapter pad 200. In other embodiments, the transverse hooks 270, 271 of the adapter pad may be integral with the adapter 199. In other embodiments, the transverse hooks 270, 271 may be attached to the adapter 199 and / or pad 200 of the adapter using adhesives or other known methods.

[00165] The adapter cushion 200 may also include a first lateral frame 272 lateral frame located on the outer surface 224 of the first upwardly directed portion 228 of the upper plate 220; and a second lateral frame hook 273 located on the outer surface 224 of the second upwardly directed portion 230 of the upper plate 220. In some embodiments, a first lateral frame hook 272 may be located on the outer surface 224 of the first transverse flange 232 of the upper plate 220; and the second transverse hook 273 of the side frame is located on the outer surface 224 of the second transverse flange 234 of the upper plate 220. The transverse hooks 272, 273 of the side frame can extend along the entire longitudinal length of the adapter pad 200 or along the portion of the longitudinal length of the adapter pad 200. In other embodiments, the transverse hooks 272, 273 of the side frame may comprise a plurality of transverse hooks of the side frame, which extend along the entire transverse length of the adapter pad 200 or at any portion thereof.

[00166] The hooks 270, 271, 272, 273 may be made of elastomeric material or any other suitable material and, in some embodiments, may serve to properly position the adapter pad 200 relative to the axle box 152 of the side frame and adapter 199. In addition, the first and the second transverse adapter hooks 270, 271 may be configured to reduce or prevent sliding between the adapter 199 and the bottom plate 240 of the adapter pad 200. Similarly, the first and second lateral hooks 272, 273 of the side frame may be configured to reduce or prevent sliding between the outer surface 224 of the upper plate 220 and the axle box 152. In some embodiments, this may reduce or prevent sliding between the mating surfaces of the adapter 199 and adapter cushions 200 and between the mating surfaces of the axle box 152 of the side frame and adapter cushion 200 during operation of the system. In addition, in some embodiments, this decrease in slip between the contacting surfaces may reduce the amount of heat generated during such slip.

[00167] As discussed above, the engaging elements can significantly reduce the relative movements between the horizontal surfaces of the adapter pad system, maintaining tight contact between the vertical mating surfaces of the adapter pad assembly. Reducing the relative movements between the axle box 152 of the side frame and the adapter pad 200 can improve the stiffness behavior of the adapter pad 200. As shown in FIG. 14, when comparing lateral stiffness, for example, in an adapter cushion system with and without hooks, an improvement can be seen at the end of the course, where instead of sliding, the adapter / axle box cushion border shows greater resistance during longer lateral movement than the adapter cushion system, which does not contains hooks. Reducing the slip between parts can also reduce the physical wear of the adapter pad system.

[00168] In some embodiments, heat may be generated when the adapter pad 200 is moved relative to the roller bearing adapter 199 and axle box 152. This heat leads to hysteresis of the cycling of the elastomeric material under shear displacement. As discussed above, excess heat can adversely affect the characteristics of the elastomeric element 360 and reduce the wear resistance of the adapter pad. As shown in FIG. 15, which compares the dynamic fatigue characteristics of the adapter cushion with and without hooks, the adapter cushion 200 with the hooks generates less heat than the adapter pillow 200 without the hooks. In some embodiments, the temperature of the adapter pad 200 will not exceed about 130 degrees Fahrenheit when the adapter pad 200 is located between the roller bearing adapter 199 and the axle box 152 of the side frame of the moving car. In some embodiments, the adapter pad system 198 may be configured to limit the temperature of the elastomer below the degradation temperature of the particular elastomeric and / or adhesive materials used in the pad structure, and in some embodiments, the adapter pad system may be configured to reduce melting of the elastomer element.

[00169] As discussed above, and as shown mainly in FIG. 16A-B and 11B-C, the elastomeric member 360 is located between the upper plate 220 and the lower plate 240. The elastomeric element 360 supports vertical loading and allows limited longitudinal, transverse and rotational movement of the upper plate 220 (supporting the side frame) relative to the lower plate 240 (supported adapter). This allows relative movement of the side frame relative to the adapter with low stiffness and, consequently, low loads compared to the sliding designs of the adapter. As shown in FIG. 17A-17D, the displacement of the upper plate 220 relative to the lower plate 240 can be measured with longitudinal displacement (Fig. 17B), lateral displacement (Fig. 17C) and rotational displacement (Fig. 17D). The adapter cushion elastomeric material 360 may be a hysteretic material and have damping of the material during cyclic displacements. This provides another energy absorbing element depending on the choice of material and damping. For example, a material with too much damping can cause overheating of the elastomeric element 360 and reduce its short-term stiffness and long-term wear resistance. The elastomeric element 360 may be formed of any suitable elastomeric material, for example rubber, with suitable strength, flexibility and stiffness characteristics. In some embodiments, the material used for the elastomeric element should have a Shore durometer hardness of 70 +/- 10 on a scale A. Elastomers that can be used may include, but are not limited to: natural rubber; nitrile; hydrogenated nitrile; butadiene; isoprene or polyurethane and can have a shore hardness of about 60 to about 80 on a scale A.

[00170] In general, the elastomeric member 360 may be attached to the upper and lower plates 220, 240 by injection molding. Typically, the upper and lower plates 220, 240 may be placed in the mold. In some embodiments, portions of the upper and lower plates 220, 240 may be coated with adhesive, which allows the adhesion of the elastomeric element 360 to the plates. In addition, in some embodiments, in certain areas of the form where elastomeric material is not required, dividers may be placed. After installation is complete, the elastomeric material can be heated and inserted into the mold, and the elastomeric material can fill the entire mold cavity, adhering to the areas coated with the adhesive. The elastomeric material may then be subject to vulcanization and / or curing.

[00171] The elastomeric member 360 may provide damping in the adapter pad 200, allowing discrete changes in stiffness and / or flexibility in the adapter pad 200 and allowing differences in damping, stiffness, flexibility, or other parameters in different parts of the adapter pad 200 to provide a suitable design.

[00172] As shown in FIG. 11A, the elastomeric member 360 includes a central portion 362 that is located in a central portion 210 of the adapter pad 200, and first and second outer elastomeric members 364, 366 that are located in respective first and second transverse flanges 216, 218. The outer elastomeric members 364 , 366, increase the shear area and volume of the elastomeric layer 360 by extending the elastomeric material beyond the envelope of the gap of the standard adapter by using transverse flanges 216, 218. This provides a large area for For the elastomeric member 360 and may increase the rigidity of the adapter pad 200.

[00173] As best shown in FIG. 16A, in a plan view, the central elastomeric portion 362 may have a generally square shape and, in some embodiments, as shown in FIG. 16A may have one or more rounded corners 363. Rounded corners throughout the elastomeric member 360 may reduce or prevent stress concentration compared to the square-shaped elastomeric member 360. As discussed above, the thickness of the elastomeric member 362 may be uniform throughout the central portion 210.

[00174] The central elastomeric portion 362 may be mainly located in the central portion 210, but in some embodiments, may also be located in the first and second upwardly directed portions 212, 214, as shown in FIG. 16B, and in the transverse flanges 216, 218. As shown in FIG. 16B, the central elastomeric member 362 may have a transverse length of about 6.7 inches, or in the range of about 6.5 inches to about 10 inches. In some embodiments, and as shown in FIG. 16B, the elastomer 360 may be located between the upper and lower plates 220, 240 in the upwardly directed portions 212, 214. In embodiments in which the elastomer 360 is located between the plates in the upwardly directed portions, it may be compressed or shifted under lateral loading. This compression of the elastomer in the upwardly directed portions 212, 214 in combination with the elastomer shear in other portions can allow the high rigidity of the adapter pad to be achieved, which can improve performance.

[00175] As best shown in FIG. 16A, in a plan view, the outer elastomeric portions 364, 366 in one or both of the first and second transverse flanges 216, 218 form an outer edge 374, 376, respectively. The outer edge 374, 376 may be located between the upper and lower plates 220, 240, so that a portion of one or both of the upper or lower plates 220, 240 extends radially outward past at least a portion of the outer edge 374, 376 of the elastomeric section.

[00176] In some embodiments, the outer edge 374, 376 may be a longitudinal outer edge (374a, 376a) (ie, may extend generally in the longitudinal direction when the adapter pad 200 is installed in the trolley system) and may include a curved section that does not have an excellent shape and is not aligned with the outer longitudinal edge of the upper and / or lower plates 220, 240. Although the expression “longitudinal outer edge” is used, it is intended to define the portion of the outer edge that extends between opposite transverse edges 280, 282 (i.e., two edges that extend laterally between the first and second transverse flanges 216, 218 and through the central portion 210), and, as discussed herein, may be curved, with each portion of the curve includes at least a vector component that is facing in the transverse direction (i.e., perpendicular to the direction of movement of the cart on which the adapter pad 200 is mounted).

[00177] For example, at least a portion 374R, 376R of the outer edge 374, 376 may be formed with a continuous radius (R) with respect to the geometric center of the adapter pad indicated by the letter “C” in FIG. 16A. In some embodiments, each outer edge 374, 376 may include two discontinuous curved edges 374R, 376R with a constant radius, the central portion between the two edges being straight or having a curvature different from those with a constant radius. In other embodiments, a portion with a constant radius can be continuous and extend from a location near both opposite transverse edges 380, 382 on the corresponding transverse flange, for example, along the entire corresponding transverse flange, or between opposite transverse edges, but in conjunction with section 374z, 376z extending from respective upwardly directed portions 212, 214 to an edge 374, 376 with radial geometry.

[00178] In some embodiments, the transverse edges 380, 382 and the longitudinal outer edges 374a, 376a and any other edge of the elastomeric portion 360 may have an inwardly recessed contour 381, as best shown in Figures 11A-11C. In some embodiments, the inwardly deepened contour 381 may have the same profile along the entire perimeter of the elastomeric element 360, although in other embodiments, the inwardly deepened contour 381 may have different profiles depending on the intended compression to which this portion of the elastomeric element 360 is subjected.

[00179] As will be understood, and as discussed herein, the elastomeric member 360 is compressed and deformed under load, and the elastomeric material is extruded radially outward near the outer edges. The inwardly recessed contour 381 minimizes or prevents deformation of the elastomeric member 360 beyond the nominal outer edge of the member 360, which in some embodiments may increase the fatigue life of the adapter pad 200.

[00180] The inwardly recessed contour 381 may include a first portion 383 that generally extends downward from the lower surface of the upper plate 220, a second portion 385 that extends generally upward from the upper surface of the lower plate 240, and a transition 384 between them. In some embodiments, one or both of the first and second sections 383, 385 may be flat (along the straight section of the elastomeric section) or linear (along curved sections of the elastomeric section) (together with the linear section) and may extend from the corresponding surface of the upper and lower plates 220, 240 at angles α and β.

[00181] In some embodiments, the first and second sections 383, 385 may extend at the same relative angles, although in other embodiments, the first and second sections 383, 385 may extend at different relative angles. In some embodiments, the angle (s) may be about 30 degrees to the nearby surface of the upper or lower plates 220, 240, for example, an angle in the range of about 15 to about 45 degrees, including all angles within this range. As shown in FIG. 11B, the central elastomeric portion 362 may likewise have a similar inwardly recessed contour 381 extending along the outer edge of the central portion.

[00182] As best shown in FIG. 11A, 11C and 16B, one or both of the upwardly directed portions 212, 214 may include a hollow portion (s) 372 in a cavity defined between the upper and lower plates 220, 240, which is an empty space in which there is substantially no an elastomeric material is provided, and which can create a gap within the elastomeric element in the respective first and / or second upwardly directed sections 212, 214. Hollow sections 372 can provide complete separation between the elastomeric element 360 located in the central section 210, an elastomeric element located in the transverse flanges 216, 218. In some embodiments, the void space may include a very thin layer of elastomeric material that contacts each of the upper and lower plates 220, 240 through the transition, which may be due to possible tool limitations, used in the molding process, but this thin layer (if any) does not significantly affect the performance of the adapter pad 200. In addition, in some embodiments, the hollow portion 372 may include small portions of elastomeric material that extend between the upper and lower plates 220, 240, but otherwise is substantially hollow. In some embodiments, the width of the hollow portion 372 may be about 0.25 inches, or in the range of about 0.1 inches to about 0.5 inches, or at least the same as the maximum lateral and rotational movement on the adapter pad 200. In some embodiments, the hollow section (s) 372 is configured to provide a transverse empty space between the upper and lower plates 220, 240 passing through the corresponding transition section 212, 214, so that the corresponding inner surfaces of the upper and lower plates 220, 240 in the transition section do not contact each other during transverse or rotational relative movement between them and / or due to transverse and / or rotational displacement during operation of a railway carriage with a pad 200 adapter Located in the desired position in the rail car truck system.

[00183] The hollow portion 372 may serve to limit bending stresses in the upper and lower plates 220, 240. The hollow portion 372 may be about 0.25 inches. With a travel range of about 0.25 inches, the upwardly directed portions of the upper and lower plates 220, 240 can contact and prevent additional relative movement. This can determine the upper limit of elastomer deformation in the transverse direction and the stress of the metal.

[00184] As will be discussed in more detail below, the elastomeric element 360 and, in particular, the external elastomeric elements 364, 366 can be made so that the rotational shear stresses of the elastomer when displaced to 41 milliradians do not exceed the transverse and longitudinal shear stresses of the elastomer when displaced up to 0.23 inches in the transverse direction and up to 0.14 inches in the longitudinal direction. For example, the external elastomeric elements 364, 366 may be configured such that any point on the curves 374R, 376R has a lesser or equal rotational shear displacement with respect to transverse or longitudinal shear displacements. And since the shear strain is directly proportional to the shear displacement, all points along the curve 374R, 376R can be subject to the same strain.

[00185] The elastomeric element 360 can be measured in the sectional plane through the center of the elastomeric material 360, centered between the inner surfaces of the upper and lower plates 220, 240. In embodiments in which there are many elastomeric elements, each element can be measured separately and measured for each element can be folded together to determine the measurement of the entire elastomeric element 360. In some embodiments, the total shear width or transverse length of the elastomeric element 360 ozhet be about 9.6 inches or in the range from about 6 inches to about 14 inches. Similarly, the total shear length or longitudinal length of the elastomeric member 360 may be about 6.9 inches, or in the range of about 6 inches to about 10 inches. The total shear perimeter or perimeter of all portions of the elastomeric member may be about 51.70 inches, or in the range of about 35 inches to about 75 inches. In some embodiments, the total surface area of the elastomeric member 360 in the shear plane may be about 55.5 square inches, or in the range of about 50 square inches to about 70 square inches. The total surface area of the elastomeric member 360 outside the central portion may be about 15.5 square inches or in the range of about 5 square inches to about 30 square inches or more than 5 square inches. Thus, the surface area of the elastomeric element in the transverse flanges 216, 218 may be about 7.75 square inches each, or in the range from about 2.5 square inches to about 15 square inches or more than 2.5 square inches.

[00186] As will be discussed in more detail below, elastomeric layers 364, 366 outside the central portion 210 may contribute to the overall stiffness of the adapter pad 200. For example, in some embodiments, elastomeric member 360 outside the central portion 210 can provide about 15%, or in the range of about 5% to about 30% of the total lateral and longitudinal stiffness of the adapter pad, and 33%, or in the range of about 15% to about 60% of the rotational stiffness of the pillow 200 adapter.

[00187] As previously discussed, the elastomeric member 360 of the adapter pad 200 provides shear resistance under load in the transverse, longitudinal and rotational directions under vertical load. This shear resistance is due to the relative movement between the upper and lower plates 220, 240 interacting through the elastomeric element 360. A simple shear deformation is defined as d / t, where d is the displacement of the elastomeric element, and t is the thickness of the elastomeric element. In some embodiments, shear deformation can reach values greater than 100% under conditions of maximum displacement. For example, in some embodiments, the transverse strain reaches 110% or 120% or 130%. In some embodiments, shear deformation does not exceed 105%, 110%, 115%, 120%, or 130% at maximum displacement.

[00188] To reduce stresses in the elastomeric member 360 at maximum shear displacement, it may be advisable to provide normal stress or compression of the elastomeric member 360 under shear stress. In some embodiments, the vertical load of the adapter pads is transferred through the axle box 152 of the side frame to the central portion 210. In addition, although the upper and lower plates 220, 240 can contact the vertical shoulders of the adapter, in some embodiments, the upper and lower plates 220, 240 are flexible, and the vertical load on the Central portion 210 is unevenly transferred to the transverse flanges 216, 218 and can create an uneven distribution of the vertical load on the elastomeric element 36 0. This can lead to less compression of the elastomeric element 360 outside the area under the axle box 152. Various methods can be used to increase the normal stress or compression in the elastomeric element 360 outside the axle box 152, for example, in transverse flanges 216, 218.

[00189] In embodiments, the elastomeric member 360, beyond the area of the axle box 152, may be compressed by more than 0.020 inches or more than 7% of the static thickness of the elastomeric member 360. In some embodiments, pre-compression by this amount provides improved fatigue life elastomeric member 360. In addition, in the embodiments discussed herein, from about 10 percent to about 30 percent of the vertical force can be distributed to each of the transverse flanges 216, 218 of the bottom Adapter ki under the influence of a vertical force to the central portion 210 cushions 200 adapter. In the embodiments described herein, the effect of the vertical load on the vertical shoulders 106 may provide a vertical force exceeding 3,000 pounds to pre-compress the elastomeric member.

[00190] In some embodiments, as shown mainly in FIG. 18, compression of the elastomeric member 360 in an area outside the axle box 152 (in the outer elastomeric members 364, 366) can be accomplished by providing an elastomeric member 360 having an uneven thickness along the length of the elastomeric member 360. For example, in some embodiments, the first and / or the second outer sections 364, 366 can be formed with a thickness X, while the central section 362 can be formed with a different or smaller thickness Y. The geometry (for example, bends through the upwardly directed sections 212, 214) of the upper and lower plates Astin 220, 240 can be formed to match the differences in thickness between X, Y, which allows the elastomeric sections in the central and external sections to contact the inner surfaces of the upper and lower plates 220, 240, if necessary. In some embodiments, the difference in thickness of the elastomeric element forming the first and / or second outer sections 364, 366 and the central section 362 can help reduce simple shear strains of the outer layers based on the forces acting in the plane that act on the adapter pad in the longitudinal, transverse and rotational directions.

[00191] In some embodiments, as shown in FIG. 18, one or both of the transverse flanges 216, 218 can be formed so that the elastomeric layers 364, 366 in them have a thickness X that is about 0.25 inches, for example, in the range from 0.15 inches to 0.30 inches, including all thicknesses in the range. In this embodiment, the thickness Y of the elastomeric layer 360 in the central portion 362 may be about 0.20 inches, for example, in the range of 0.15 inches to 0.25 inches, including all thicknesses in the range. The thickness of the elastomeric layers discussed herein refers to the static thickness of the elastomeric layers or the thickness of the elastomeric layers without an external load on the elastomeric layers. One or both of the transverse flange sections 364, 366 and the central section 362 can have different thicknesses, the upper sections being thinner than the central section, which can provide the desired effect, as a rule, increasing the load or compression of one or both transverse flange sections 364, 366, due to the properties of the material of the elastomeric layer additionally increases the strength and wear resistance based on the expected load during operation of a railway carriage.

[00192] In some embodiments, as shown in FIG. 18, the adapter pad 200 may be injection molded without connecting the top plate 220 (as shown in FIG. 18) or alternatively the bottom plate 240 with the elastomeric member 360. After curing the elastomeric member 360, the top plate 220 (as shown in FIG. 18) or alternatively, the bottom plate 240 may be attached or attached to the elastomeric element. Since the outer elastomeric elements 364, 366 are thicker than the central elastomeric element 362, the transverse flanges 216, 218 must be compressed to fasten or attach the upper plate 220 (as shown in Fig. 24) or alternatively the lower plate 240 to the elastomeric element. In some embodiments, the central elastomeric member 362 will respond to a compression load while keeping the wings in a state of compression deformation.

[00193] In some embodiments, as shown in FIG. 19-23, compression of the elastomeric element 360 in an area outside the axle box 152 can be achieved by forming an elastomeric element 360 with gaps in the central portion 362. In some embodiments, for example, the central portion 362 includes one or other embodiments elongated gaps 868 that partially or completely divide the central portion 362 into a plurality of portions 862a, 862b, 862c, 862d, 862e, as shown in FIG. 19. One or a plurality (the expression “plurality” is used below for convenience, although one clearance is also assumed) of the clearances 868 together form a plurality of gaps in the central portion 362. When the adapter pad 200 is installed between the side frame and the bearing adapter 199, the central portion 210 of the pad 200 the adapter can support a significant compressive force, which is perceived relatively compressible elastomeric section 360 (compared with the upper and lower plates 220, 240), which tends to deform and expand l elastomeric element 360 in the transverse direction and the longitudinal direction (due to vertical compression of the material). The presence of multiple gaps 868 may provide an allocated volume for lateral expansion (in embodiments where each of the multiple gaps 868 extends in the longitudinal direction). Similarly, in embodiments in which a plurality of gaps extends additionally or instead in the transverse direction, the presence of gaps 868 provides an allocated volume for longitudinal expansion.

[00194] As best shown in FIG. 19, in some embodiments, a plurality of gaps 868 extend longitudinally between opposing transverse edges 880, 882 of the elastomeric portion 860 and parallel to each other. In some embodiments, multiple gaps 868 communicate through both of the first and second longitudinal edges 880, 882 when the adapter pad 200 is in an unloaded configuration. Under load, all or part of the multiple gaps 868 can be deformed (as discussed above), so that only part of the corresponding gap 868 communicates through the corresponding longitudinal edge 880, 882, or in some embodiments, substantially the entire gap 868 can be closed, crossing the longitudinal edge 880, 882, so that no visual aperture (which is visible from the corresponding edge 880, 882 in an unloaded configuration) can be seen in the gap 868.

[00195] In some embodiments, as shown in FIG. 19 and 22, each of the plurality of gaps 868 can be formed with a uniform cross section along its length, and either all of the plurality of gaps 868 can be formed with the same cross section (in an unloaded state), or each of the plurality of gaps 868 can be formed with a constant cross section along its length.

[00196] Figures 20A-20C illustrate various types of cross sections of a plurality of gaps 868. It is generally contemplated that a plurality of gaps 868 includes one or more curved or planar sides, and each of the plurality of gaps 868 may include a combination of curved and planar elements . For example, a plurality of gaps 868a have a circular cross section or include curved sides. In some embodiments, opposing sides (which extend between the upper and lower plates 220, 240) may have the same size and geometry, although, as shown in FIG. 20A, one side may have a shape or size different from the opposite side (see 866 ′ and 868ʺ in FIG. 20A).

[00197] Figure 20B depicts alternative gaps 868c that are generally oval in shape. Figure 20C depicts alternative gaps 868d that are in the form of a truncated rhombus with two opposite flat sides (the truncated portion being in contact with the bottom plate 240). Figures 21A-21C provide schematic representations of a possible shape of a different set of gaps 868 when exposed to a load (F) on adapter pad 200.

[00198] In some embodiments, and as shown in FIG. 22, a plurality of gaps 868e pass through the elastomeric element 860 only at a partial longitudinal distance and, as shown, do not reach the longitudinal edges 880, 882, although other arrangements are provided (for example, extending to one of the two longitudinal edges 880, 882 or positioning the ends closer to one of the two longitudinal edges 880, 882). In this embodiment, the gaps 868d may have a size and shape based on various sizes and shapes discussed above.

[00199] In other embodiments shown in FIG. 23, the plurality of gaps 868f may extend a thickness that is less than the total distance between the upper plate 220 and the lower plate 240, the elastomeric element portion being vertically disposed relative to one or more of the plurality of gaps 868f and in contact with one or both of the upper and lower plates 220, 240. As shown in FIG. 23, the gap 868f is in contact with the lower surface of the upper plate 220, but is not in contact with the lower plate 240.

[00200] As best shown in FIG. 23, the inner surfaces of the upper or lower plate 220, 240 may include a recessed portion 825a located along portions of the upper or lower plate 220, 240 that communicate with a plurality of gaps 868. Recessed portions 825a may be provided to accommodate a tool (eg, a shaft or other type of molding equipment known in the art) for the elastomeric portion to form gaps 868 relative to the upper or lower plate 220, 240. The recessed portion 825a may further provide space GUSTs for expansion / deformation of the elastomeric member 860 with a load to minimize the size of the gaps 868, providing advantages space for expansion / deformation, if appropriate.

[00201] In addition, there are other ways to increase the compression of the elastomeric element 360 in the transverse flanges 216, 218. For example, as shown in FIG. 24, in some embodiments, transverse flanges 216, 218 can be compressed together after inserting elastomeric elements 364, 366 between the upper and lower plates 220, 240. Compressing the upper and lower plates 220, 240 together can cause plastic deformation of the steel. Plastic deformation of the upper and lower plates 220, 240 can cause normal stress in the outer elastomeric layers 364, 366 and can increase compression. The compression of the upper and lower plates 220, 240 can be performed using a matrix or other suitable equipment. In this context, the term “insert” may include a number of processes, including the insertion of an elastomer using an injection molding process or a molding process and other known techniques.

[00202] In other embodiments, for example, compression in the transverse flanges 216, 218 can be achieved by manufacturing the transverse flanges 216, 218 of the upper and lower plates 220, 240 at an angle to each other and further molding the flanges in a common parallel position. For example, the upper plate 220 can be made so that the transverse flanges 232, 234 are directed outward and downward, and the transverse flanges 252, 254 of the lower plate 240 are directed outward and upward until the adapter pad 200 is assembled. Thus, in the initial production, the transverse flanges of the upper and lower plates are not parallel, but are located at an angle to each other. Then the plates 220, 240 are connected to the elastomeric section 360, and the transverse flanges 232, 234, 252, 254 are elastically bent, generally aligned parallel to each other. In some embodiments, this step may be performed using an injection molding machine in which an elastic member 360 is inserted into the mold. After vulcanization of the adapter pad in the transverse projecting flanges, elastic deformation can be ensured, which exerts a normal load on the external elastomeric layers 364, 366, which can create compression deformation.

[00203] In other embodiments, as shown in FIG. 25 and 26, the compression of the elastomeric member 360 in the transverse flanges 216, 218 can be increased by using compression gaskets in or under the transverse flanges 216, 218. Compression gaskets can be used so that the vertical load on the vertical shoulders 106 provides a vertical force exceeding 3,000 pounds, so that from about 10 percent to about 30 percent of the vertical force is distributed to each of the transverse flanges 216, 218 of the adapter pad when exposed to a vertical forces on the central portion 210 of the adapter pad 200. In some embodiments, compression pads can cause the distribution of most of the vertical load of the car from the central elastomeric layer 360 to the outer elastomeric layers 364, 366. As shown in FIG. 25, the first adapter compression gasket 290 may be located between the upper surface of the vertical shoulder of the roller bearing adapter 199 and the outer surface 244 of the first transverse flange 216 of the lower plate 240. Similarly, although not shown in FIG., The second adapter compression gasket 290 may be similar located relative to the second transverse flange 218 (not shown). The compression gaskets 290 of the adapter may have a thickness of about 0.05 inches or in the range from about 0.06 inches to about 0.18 inches. The compression gaskets discussed herein can have any number of different shapes and configurations to provide the necessary loads to compress the external elastomer. For example, compression pads may be rectangular, square, trapezoidal, pyramidal, may have a hollow cross section and may be a plurality of compression pads. In addition, the compression pads discussed herein may be integral with the adapter pad during molding, may be integral with the roller bearing adapter, or may be added to the roller bearing adapter system after the molding process.

[00204] As shown, for example, in FIG. 25A-I, the compression gaskets discussed herein may have several different shapes and configurations. As shown in FIG. 25A, the compression gaskets 290 may be substantially rectangular and may have a width equal to or less than the width of the outer surface 244 of the transverse flange 252, 254 of the lower plate 240. Similarly, the compression gaskets 290 shown in FIG. 25A may have a length less than or equal to the length of the outer surface 244 of the transverse flange 252, 254 of the lower plate 240. The compression gaskets 290 may have a constant or variable thickness. As shown in FIG. 25B, 25C and 25D, the compression gaskets 290 may have a curved, trapezoidal, or triangular cross-sectional shape. Furthermore, as shown in FIG. 25E and 25D, the compression gaskets 290 may have a raised central portion 295, which may be generally curved, as shown in FIG. 25E, or generally triangular, as shown in FIG. 25F, or any other suitable form. As shown in FIG. 25G, the compression gaskets 290 may include a hollow portion 296. Furthermore, as shown in FIG. 25H and 25I, compression pads 290 may include a plurality of compression pads.

[00205] As shown in FIG. 26, adapter pad 200 may also include compression pads between the elastomeric member 360 and the upper or lower plate 220, 240. As shown in FIG. 26, adapter pad 200 may include a first upper adapter pad compression gasket 291 located in the first transverse flange 216 between the upper plate 220 and the first external elastomeric member 364. Similarly, although not shown in FIG., In the second transverse flange 218 between the upper plate 220 and the second outer elastomeric element 366, a second upper adapter pad gasket 291 may be located. In addition, although this is not shown in Fig., Similar first and second lower compression pads of the adapter cushion may be located in the first and second transverse flanges 216, 218 between the elastomeric member 360 and the lower plate 240. The upper and lower compression pads 291 of the adapter cushion may have a thickness of about 0.05 inches or in the range of about 0.06 inches to about 0.18 inches.

[00206] To accommodate the upper or lower compression pads 291 of the adapter pad shown in FIG. 26, adapter pad 200 can be injection molded without applying adhesive to one of the upper or lower plates 220, 240 in transverse flanges 216, 218. This can prevent the outer elastomeric layer 364, 366 from sticking to the upper or lower plate 220 240. After curing, the upper or lower compression pads 291 of the adapter pad can be inserted between the external elastomer 364, 366 and the upper or lower plate 220, 240. As discussed above, they can compress the elastomeric element 360 into you blunt transverse flanges 216, 218, increasing the normal voltage.

[00207] As discussed above, during the test it was determined that the performance of the adapter pad system 198 is a function of the stiffness of the adapter pad 200. In particular, in some embodiments, it is determined that the performance of the adapter pad, including the design life, can be improved by increasing the rigidity of the adapter pad system 198 (measured in pounds of force per inch of deformation).

[00208] The physical measurement of the stiffness of the cushion can be determined by cycling the adapter cushion 200 in three main directions: transverse, longitudinal and rotational; while maintaining a constant vertical load on the pillow, usually of 35,000 pounds. The force to displace the cushion by the relative displacement of the cushion is recorded throughout the measurement test. Then, the test data can be collected and plotted against force and displacement, an example of which is shown in FIG. 27. Then stiffness, damping and hysteresis for each direction of movement can be determined using the following methods. The stiffness of the pad 200 can be determined by determining the upper and lower bounds that capture the linear portion of the curve of the relationship between force and displacement, and then calculating the slope of the line of best fit between the upper and lower bounds for the upper and lower portions of the curve. Then stiffness is determined by averaging the upper and lower slopes. As discussed above, the longitudinal stiffness is measured in the direction of the rails or tracks, the transverse stiffness is measured perpendicular to the direction of the tracks, and the rotational stiffness is measured as the resistance to rotation of the adapter around the vertical axis on the longitudinal and transverse axial lines of the axle box hole (indicated by the letter “C” in Fig. 16A) . Hysteresis, an example of which is shown in FIG. 27 is determined by determining the upper and lower intersection points of the Y axis and subtracting the lower intersection point of the Y axis from the upper intersection point of the Y axis. The damping shown in FIG. 27 is determined by determining the area inside the loop of the relationship between force and displacement. The amount of cushion damping over a given range of displacements is directly proportional to the area enclosed in the loop at the desired frequency.

[00209] The damping target for the embodiments disclosed herein is from 0.10 to 0.30 tan δ at a target hardness of the rubber / elastomeric material of the durometer from 60A to 80A. Tan δ is a measure of the damping of a material when exposed to cyclic loads, defined as the ratio of the phase shifted load (90 degrees sinusoidal load) to the phase load (0 degrees). Typical values for elastomers can range from 0.04 to 0.35.

[00210] A more direct measure of the energy absorption of the adapter pad is the area of the hysteresis loop per cycle. For the embodiments described herein, hysteretic energy absorption can be estimated as π3GTanδε ² , where G is the shear modulus of ~ 360 psi, Tan δ ~ 0.3, and ε is the strain during wobble, ~ 100% = 1 . At a frequency of 4 Hz, the energy absorption will be about 4,070 inch-pounds / second. A reasonable range may be +/- 25%.

[00211] As discussed herein, some embodiments include an elastomeric element 360 (portions 364, and 366) in shear outside the area under axle box 152. In such embodiments, there may be more elastomeric material than can be used in shear than in a conventional adapter pillow. This can ensure that the increased rigidity of the adapter pad 200 is achieved without reducing the shear thickness or increasing the durometer elastomer hardness. Reducing the shear thickness and / or increasing the hardness of the elastomer by the durometer can increase the deformation and reduce the useful life of the pillow. Thus, the adapter pad 200 can increase the rigidity of the adapter pad system 198, which can improve the overall performance of a railroad car while increasing the useful life of the adapter pad 200. Outer elastomeric layers 364, 366 can increase the rotational stiffness of the adapter pad 200 by providing additional elastomer at a distance remote from the axis of rotation. In some embodiments, for example, the outer elastomeric layers 364, 366 can provide about 15% or from about 10% to about 20% or more than 10% of the total lateral and longitudinal stiffness of the adapter pad 200 and can provide about 33% or from about 25 % to about 40% or more than 25% of the rotational stiffness of the pad 200 of the adapter.

[00212] The embodiments disclosed herein may have high lateral and longitudinal stiffness without much hysteresis of the relationship between force and displacement. Hysteresis is proportional to the energy dissipated during the displacement cycles, and may be lost in the form of heat or noise. In general, the higher the hysteresis, the greater the increase in temperature of the adapter pad 200 and the less the fatigue life. The embodiments disclosed herein achieve high rigidity of the adapter cushion while increasing fatigue life by minimizing hysteresis and ensuring the cushion is offset by the maximum value set by AAR: 41 milliradians in the rotational direction, 0.23 inches in the transverse direction, and 0.14 inches in the longitudinal direction.

[00213] In the embodiments disclosed herein, an increase in force may be required to bias the upper plate 220 relative to the lower plate 240 by a large amount. The thickness, length, and amount of elastomeric material in the hollow portion 372 can be adjusted to change the slope and shape of the graphs of the relationship between force and displacement. In some embodiments, other stiffness properties of the elastomeric material of the pillow located adjacent to the upwardly directed wings of the adapter are possible, compared with the properties of the elastomeric material located in the central portion of the pillow of the adapter.

[00214] Using the test methods described above, exemplary measurements and test results of the embodiments disclosed herein are shown in Table 2 below. It should be understood that these embodiments are exemplary and that other structural embodiments with other test results may exist. .

table 2

Embodiments Described herein Normal Elastomer Area ( ² inches) 55.5 inch ²
or from about 50 inches ² to about 70 inches ² Normal elastomer area outside contact with axle box ( ² inches) 15.5 inch ²
or about 5 inches ² to about 30 inches ² Pillow Elastomer Shear Width (Transverse Length) (inches) or from about 6 inches to about 14 inches Elastic Pillow Shear Length (Longitudinal Length) (inches) or from about 6 inches to about 10 inches Transverse stiffness
(measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) 60 thousand pounds / inch
or from about 45 thousand pounds / inch to about 80 thousand pounds / inch
or at least 45 thousand pounds / inch Longitudinal stiffness
(measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) 64 thousand pounds / inch
or from about 45 thousand pounds / inch to about 80 thousand pounds / inch
or at least 45 thousand pounds / inch Rotational stiffness
(measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) 670 thousand pounds × inch / mrad
or from about 250 thousand pounds × inch / mrad to about 840 thousand pounds × inch / mrad
or at least 250 thousand pounds × inch / mrad Vertical stiffness at least 5,000 thousand pounds per inch Transverse hysteresis (measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) or from about 3,750 pounds to about 6,250 pounds
or less than 6,000 pounds Longitudinal hysteresis
(measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) or from about 375 pounds to about 1,500 pounds
or less than 1,500 pounds Rotational hysteresis
(measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) 12,000 psi
or from about 9,000 psi to about 16,000 psi
or less than 16,000 psi The shift perimeter of the Central elastomeric layer or from about 20 inches to about 30 inches The shear perimeter of the outer elastomeric layers 13.1 inches each
or about 8 to about 18 inches each The shear perimeter of the total elastomeric layer or from about 35 inches to about 75 inches Form factor of the central elastomeric layer 8.3
or from about 6 to about 10 Form Factor of External Elastomeric Layers 1.6 each
or from about 0.5 to about 3 each General form factor 4,5
or from about 2.5 to about 7

[00215] An additional embodiment of an adapter pad 400 is shown in FIG. 28-43. An embodiment of the adapter pad 400 shown in FIG. 28-43, in many respects similar to the adapter cushion options discussed earlier. As described above, the adapter cushion 400 is adapted to be placed between the roller bearing adapter 199 (as shown in FIGS. 36A-36E) and the axle box 152 of the side frame 4 and can interact with them. As shown in FIG. 28-43, adapter pad 400 generally includes an upper element or upper plate 420 having an inner surface 422 and an outer surface 424, a lower element or lower plate 440 having an inner surface 442 and an outer surface 444, and an elastomeric element 560 located between the inner surfaces 422, 442 of the upper and lower plates 420, 440 along the portion of the adapter pad 400. The adapter cushion 400 includes a central portion 410 that is located below the lower surface of the axle plate 152, with each plate 420, 440 having a corresponding central portion 426, 446. The adapter pillow 400 further includes first and second upwardly extending portions 412, 414 and the first and second transverse flanges 416, 418. The upper plate 420 has a corresponding first and second upwardly directed portions 428, 430 protruding upward from opposite edges of the central portion 426 of the upper plate 420, the first transverse a flange 432 protruding outward from the first upwardly extending portion and a second transverse flange 434 protruding outwardly from the second upwardly extending portion 430. Similarly, the lower plate 440 has respective first and second upwardly extending portions 448,450 protruding upward from opposite edges of the central section 446 of the lower plate 440, a first transverse flange 452 protruding outward from the first upwardly directed portion, and a second transverse flange 454 protruding outwardly from the second upwardly directed portion 450. Under the condition of the trolley system, the transverse flanges 416, 418 extend laterally outside the axle box 152, and the central portion 410 is located under the axle box 152. The first and second upward sections 412, 414 are located between the central portion 410 and the corresponding first and second transverse flanges 416, 418 and provide a transition between them.

[00216] As described above with respect to other embodiments, the central portion 410 may mainly include three parts, including a central portion of the upper plate 426, a central portion of the lower plate 446, and an elastomeric member 560 located between them. As discussed above, an adapter pad 400 is located between the axle box 152 of the side frame, which generally has a substantially flat horizontal contact surface, and the roller bearing adapter 199, which may generally have a curved or convex arch. As shown in FIG. 30, the central portion 446 of the lower plate 440 may have a curved lower surface such that the outer surface 444 generally repeats the bending or convexity of the adapter 199. In particular, in some embodiments, the central portion 446 may have a greater thickness towards the edges 461, 462 of the central section 446 than the center of the central section 446. As described above, the thickness in the center of the central section 246 may be about 0.15 inches or in the range from about 0.06 inches to about 0.35 inches, and the thickness at the edges 461, 462 may be about 0.26 inches or in the range of about 0.15 inches to about 0.5 inches.

[00217] In some embodiments, the central portion 426 of the upper plate 420 may include an outer surface 424 and an inner surface 422 that are substantially horizontal and parallel, as shown in FIG. 30. The thickness of the central portion 426 of the upper plate 420 may be about 0.25 inches or in the range of about 0.15 inches to about 0.5 inches. In such a system, the thickness of the elastomeric portion 560 may be substantially the same throughout the central portion 410, which in some embodiments may improve performance.

[00218] With further reference to FIG. 31, the first and second upwardly directed portions 428, 430 of the upper plate 420 may include an outer flat portion 428a, 430a (only the first upwardly directed portion is shown in FIG. 31) and an inner flat portion 428d, 430d. In some embodiments, the planar portions 428a, 430a and 428d, 430d may extend at an angle Δ relative to a plane P that extends along the outer surface 424 of the central portion 426. In some embodiments, the angle Δ may be an obtuse angle, and in some embodiments the angle may be in the range of from about 95 degrees to about 115 degrees, for example, 105 degrees or any other angle within this range. As described in more detail below, in embodiments in which the first and / or second upwardly directed portions 412, 414 include a hook, a flat surface may surround one or both sides of the hook or may alternatively be positioned relative to the hook. The first and second upwardly directed portions 428, 430 of the upper plate 420 may also include lower curved portions 428b, 430b and 428e, 430e, which are the transition between the central portion 426 and the flat portions 428a, 430a and 428d, 430d. Similarly, the first and second upwardly directed portions 428, 430 of the upper plate 420 may also include upper curved portions 428c, 430c and 428f, 430f, which are the transition between the transverse flanges 432, 434 and the planar portions 428a, 430a and 428d. 430d. The upper or lower curved sections 428b, 430b, 428e, 430e, 428c, 430c, 428f and 430f may be formed with constant curvature and / or variable curvature. The lower plate 440 may include similar planar sections and upper and lower curved sections. In some embodiments, upwardly directed portions 412, 414 may not include a planar portion and may be formed with constant curvature and / or variable curvature.

[00219] With further reference to FIG. 30 and 31, the first and second transverse flanges 416, 418 can extend laterally beyond the side frame 4 and are located at a vertical height or in a plane that is different or located above a central portion 410 located below and in contact with the axle box 152. Accordingly, the first and second transverse flanges 416, 418 are located in a vertically raised position relative to the central portion 410. The transverse protruding flanges 416, 418 may provide a large area for the elastomer 560 and, as discussed above, could To increase rigidity of a pillow 400 adapter. In some embodiments, the outer surface 444 of the first and second transverse flanges 452, 454 of the lower plate 440 may be about 0.92 inches higher than the outer surface 444 of the lower edge of the lower plate 440 or in the range of about 0.25 inch to about 2 inches. The first and second transverse flanges 416, 418 may include flat and horizontal outer surfaces 424, 444, which may be parallel to the outer surface 444 of the central portion 426. In some embodiments, the outer surface 444 of the first and second transverse flanges 452, 454 of the lower plate 440 can rely on vertical shoulders 106 of roller bearing adapter 199. In other embodiments, the outer surface 444 of the first and second transverse flanges 452, 454 of the bottom plate 440 does not contact the vertical shoulders 106. In other embodiments, the outer surface 444 of the first and second transverse flanges 452, 454 of the lower plate 440 may indirectly contact the vertical shoulders 106 through another element, such as compression pad 290. As discussed above, in some embodiments, about 2,500 pounds or about 5 percent to about 30 percent of the vertical force pedestal roof 152 may be distributed to each of the transverse flanges 416, 418 of the adapter pad upon application of a vertical force to the central portion 410 of the adapter pad.

[00220] Although an embodiment of the adapter pad 400 shown in at least FIG. 28-43 includes upwardly extending portions 412, 414 and transverse flanges 416, 418; these portions are optionally included in all embodiments. In some embodiments, the central portion 410 may be used without transverse flanges 416, 418 and / or without upwardly extending portions 412, 414, although such designs may affect performance. In an embodiment, the transverse flanges 416, 418 may extend from the central portion without upwardly extending portions and without compromising performance. Similarly, in some embodiments, the transverse flanges may extend beyond the central portion, but in the same plane as the central portion. In other embodiments, the adapter pad 400 may include downwardly directed portions that can be connected to the transverse flanges.

[00221] As shown, for example, in FIG. 29, in which the upper 420 and lower 440 plates are shown in dashed lines, the upper and lower plates 420, 440 may include transverse edges 480a, 480b, 482a and 482b. The upper and lower plates 420, 440 may also include longitudinal edges 484a, 484b, 486a and 486b. The edges 480a, 480b, 482a, 482b, 484a, 484b, 486a and 486b, when viewed from the side or front or rear, may be straight or may include curved or angled sections. As shown, for example, mainly in side views in FIG. 30-33 (including Figures 31A, 31B, 33A and 33B), the edges 480a, 480b, 482a, 482b, 484a, 484b, 486a and 486b of each of the upper and lower plates 420 and 440 may have a shape where the edges are folded (FIG. 31, 31A 33, and 33A) or are located at an angle (FIG. 33A, and 33B) inward from the outer surfaces 424, 444 to the inner surfaces 422, 442 of the plates 420, 440, respectively. Furthermore, as shown mainly in FIG. 31A, 31B, 33A, and 33B, one or more edges 480a, 480b, 482a, 482b, 484a, 484b, 486a, and 486b may include a substantially vertical portion. The substantially vertical portions may be adjacent to the outer surfaces 424, 444 before the edges 480a, 480b, 482a, 482b, 484a, 484b begin to bend (FIGS. 31, 31A 33 and 33A) or tilt at an angle (FIG. 31B, and 33B) inward from the outer surfaces 424, 444 to the inner surfaces 422, 442 of the plates 420, 440. In other embodiments, the vertical section does not have to be vertical, for example, it can be located at a different angle and / or follow a different curve compared with the rest of the edges 480a, 480b, 482a, 482b, 484a, 484b 486a and 486b. One or more perimeter portions of the upper and lower plates 420, 440, including the edges 480a, 480b, 482a, 482b, 484a, 484b 486a and 486b, may have a continuous radius. In some embodiments, the continuous radius may be a radius of about 0.25 inches or more than half the thickness of the plate. In addition, one or more sections of the edges 480a, 480b, 482a, 482b, 484a, 484b 486a and 486b of the upper and lower plates 420, 440 may have a spline profile of curvature along the perimeter, including one or more sections with a variable radius and / or flat plots. The radial portions of the edges 480a, 480b, 482a, 482b, 484a, 484b 486a and 486b of the upper and lower plates 420, 440 may extend at a contact angle θ relative to the inner surfaces 422, 442 of the upper and lower plates 420, 440. In some embodiments, the angle θ may be an angle of about 25 degrees, or in the range of about 10 degrees to about 40 degrees. In some embodiments, the spline profile of the curvature will be tangent at a distance of 0.38 inches from the outermost portions of the edges 480a, 480b, 482a, 482b, 484a, 484b, 486a and 486b of the upper and lower plates 420, 440, or from about 0.12 inches to about 0.6 inches from the outermost edges. In some embodiments, the edges 480a, 480b, 482a, 482b, 484a, 484b, 486a, and 486b may extend from the outer surfaces 424, 444 of the upper and lower plates 420, 440 at an angle substantially perpendicular to the outer surfaces 424, 444, and extend from the inner surfaces 422, 442 of the upper and lower plates 420, 440 substantially at an angle of contact with the inner surfaces 442, 444. In addition, in such embodiments, some portions of the edges 480a, 480b, 482a, 482b, 484a, 484b, 486a and 486b may be not perpendicular or not tangent to internal or external surfaces 422, 442, 442, 44 4. For example, as shown in FIG. 33, the edge 482a may not extend perpendicular to the outer surface 444 around the entire perimeter of the upper and lower plates 420, 440.

[00222] In other embodiments, and as discussed above, the perimeter of the upper and lower plates 420, 440 may be configured such that at the edges 480a, 480b, 482a, 482b, 484a, 484b, 486a and 486b, the outer surfaces 424, 444 extend further than a substantially flat portion of the inner surfaces 422, 442. For example, in some embodiments, a beveled or angled edge may be used around the perimeter of the plate.

[00223] In some embodiments, all of the transverse and / or longitudinal edges 480a, 480b, 482a, 482b, 484a, 484b, 486a and 486b of the transverse flanges of the upper and lower plates 420, 440 are aligned along one vertical plane, as best shown in FIG. . 30-33. In these embodiments, the transverse length of the transverse flange of the lower plate 440 is less than the transverse length of the transverse flange of the upper plate 420.

[00224] In some embodiments, the outer edges 484a, 484b, 486a, 486b, when viewed from above, and as shown in FIG. 29B may include one or more curved sections. For example, at least a portion 484R, 486R of the outer edge 484a, 484b, 486a, 486b may be formed with a continuous radius (R) with respect to the geometric center of the adapter pad. In some embodiments, each outer edge 484a, 484b, 486a, 486b may include two interrupted curved edges 484R, 486R with a constant radius, the central portion between the two edges may be straight or have a curvature different from those with a constant radius. In other embodiments, a constant radius portion may be continuous and extend from a location near the opposing transverse edges 480a, 480b, 482a, 482b.

[00225] In some embodiments, any point on the transverse edge when the upper plate is rotated relative to the lower plate to 41 milliradians from the neutral position of the roller bearing adapter may have a linear displacement of less than or equal to 0.234. In addition, in some embodiments, any point on the transverse edge when the upper plate is rotated relative to the lower plate to 41 milliradians from the neutral position has a linear displacement less than or equal to the maximum longitudinal displacement and maximum transverse displacement. As discussed above with respect to other embodiments, the upper and lower plates 420, 440 may be made of one or more different types of alloys with suitable strength and other characteristics. For example, plates 420, 440 may be made of ASTM A36 steel plate or steel with strength equivalent or greater than ASTM A-572. In some embodiments, the entire upper plate 420 and / or lower plate 440 is formed (by casting, machining, pressing, rolling, stamping, forging, or another suitable metal forming operation) from one monolithic element. In some embodiments, plates 420, 440 may be made of a material with a constant thickness. In other embodiments, plates 420, 440 have a variable thickness. For example, as shown in FIG. 30, and as described above, the lower plate 440 may be thinner toward the center of the central portion 446. In addition, for example, in some embodiments, the transverse flanges 432, 434, 452, 454 may have a thickness greater or less than the thickness of the central section 426, 446.

[00226] As discussed above with respect to other embodiments, and as shown mainly in FIG. 30-33, an elastomeric element 560 is located between the upper plate 420 and the lower plate 440. As will be discussed in more detail below, the elastomeric element 560 can extend outside the upper and lower plates 420, 440 and can extend beyond the transverse and longitudinal edges of the plates. For example, the elastomeric member may extend laterally and / or longitudinally by at least 0.05 inches or in the range of about 0.01 inches to 0.25 inches beyond the respective transverse and longitudinal edges of the plates. The elastomeric element 560 supports vertical loading and allows limited longitudinal, lateral and rotational movement of the upper plate 420 (supporting the side frame) relative to the lower plate 440 (supported by the adapter). This allows relative movement of the side frame relative to the adapter with low stiffness and, consequently, low loads compared to the sliding designs of the adapter. As discussed above, the movement of the upper plate 420 relative to the lower plate 440 can be measured with longitudinal displacement (Fig. 17B), lateral displacement (Fig. 17C) and rotational displacement (Fig. 17D). The adapter pad elastomeric material 560 may be a material as previously discussed.

[00227] In general, the elastomeric element 560 can be attached to the upper and lower plates 420, 440 by injection molding. Typically, the upper and lower plates 420, 440 may be placed in the mold. In some embodiments, portions of the upper and lower plates 420, 440 may be coated with adhesive, which allows the adhesion of the elastomeric element 560 to the plates. In addition, in some embodiments, in certain areas of the form where elastomeric material is not required, dividers may be placed. After installation is complete, the elastomeric material can be heated and inserted into the mold, and the elastomeric material can fill the entire mold cavity, adhering to the areas coated with the adhesive. In some embodiments, the upper plate 420 and / or the lower plate 440 may include one or more openings allowing elastomeric material to pass through the corresponding plate during molding. The elastomeric material may then be subject to vulcanization and / or curing.

[00228] As previously discussed, the elastomeric member 560 can provide damping in the adapter pad 400, allowing discrete changes in stiffness and / or flexibility in the adapter pad 400 and allowing differences in damping, stiffness, flexibility, or other parameters in other portions of the adapter pad 400 to provide suitable designs.

[00229] As shown in FIG. 30, the elastomeric element 560 may include a central portion 562, which is located in the central portion 410 of the adapter pad 400, and first and second external elastomeric elements 564, 566, which are located in respective first and second transverse flanges 416, 418. The external elastomeric elements 564, 566, increase the shear area and volume of the elastomeric layer 560 by extending the elastomeric material beyond the envelope of the gap of the standard adapter by using transverse flanges 416, 418. This provides a large area ad to the elastomeric member 560, and can increase the rigidity of the adapter 400 cushions.

[00230] The central elastomeric portion 562 may have a generally square shape and in some embodiments may have one or more rounded corners. Rounded corners throughout the elastomeric element 560 can reduce or prevent stress concentration compared to the elastomeric element 560 with square angles. As discussed above, the elastomeric member 562 may have a uniform thickness throughout the central portion 410.

[00231] The central elastomeric portion 562 may be mainly located in the central portion 410, but in some embodiments, may also be located in the first and second upward portions 412, 414, as shown in FIG. 30 and 31, and in the transverse flanges 416, 418. The central elastomeric element 562 may have dimensions similar to the central elastomeric elements discussed above. In some embodiments, and as shown in FIG. 30 and 31, the elastomer 560 may be located between the upper and lower plates 420, 440 in the upwardly directed portions 412, 414. In embodiments in which the elastomer 560 is located between the plates in the upwardly directed portions, it may be compressed or shifted under lateral loading. This compression of the elastomer in the upwardly directed portions 412, 414, in combination with the elastomer shear in the other portions, can allow for high rigidity of the adapter pad, which can improve performance.

[00232] As best shown in FIG. 29B, in a plan view, the outer elastomeric portions 564, 566, at least a portion of which is in one or both of the first and second transverse flanges 416, 418, form an outer longitudinal edge 574, 576, respectively. The outer longitudinal edge 574, 576 of the elastomeric section may extend outward beyond the upper and lower plates 420, 440. The distance by which the outer edge 574, 576 of the elastomeric section extends beyond the edges of the upper and lower plates 420, 440, or may vary along the length of the edge. The elastomeric section can also form transverse edges 578, 580. The outer transverse edges 578, 580 of the elastomeric section can extend outward beyond the upper and lower plates 420, 440. The distance by which the outer edge 578, 580 of the elastomeric section extends beyond the edges of the upper and lower plates 420, 440 may be substantially the same or may vary along the length of the edge. One or more edges 574, 576, 578, 580 may be substantially straight in the vertical direction, as shown, for example, in FIG. 28.

[00233] As described above with respect to other embodiments, the outer surfaces of the plates 420, 440 may be coated with an elastomeric material 565, which may be material in contact with the axle box 152. The elastomeric coating 565 may be formed with a flat outer surface, which repeats the geometric profile of the steel section of the upper plate 420, and may have a uniform thickness either over the entire upper plate 420, or in other embodiments, a uniform thickness within individual sections along dams, for example, uniform thickness on the central portion 410, uniform thickness (possibly different or possibly the same) on one or both transverse flanges 432, 434, uniform thickness (possibly different or, possibly the same) on one or both up sections 428, 430, etc.

[00234] In some embodiments, all or most of the adapter pad 400 may be coated with an elastomeric material 565, which may be integrally formed with the elastomer element 560. For example, in some embodiments, most of the adapter pad 400 may have an elastomeric coating material 565, with the exception of those portions of the adapter cushion 400 that are in contact with the axle box 152 and the upper surface of the adapter 199, for example, the outer surface of the upper and lower plates 420, 440. In some, In embodiments, for example, a coating of elastomeric material 565 can contact the axle box 152, the side frame 4 and the roller bearing adapter 199, including the axial convex surface 102 and the vertical shoulders 106. In other embodiments, for example, portions of the adapter pad 400 that are in contact with axle box 152, side frame 4 and roller bearing adapter 199 may not be coated with elastomeric material. As discussed herein, elastomeric layer 565 can provide damping and calibrated flexibility of the pad as well as a compressible surface to minimize wear between the adapter pad 400, the axle box 152 and the roller bearing adapter 199. The elastomeric coating 565 may repeat the shape of the outer surfaces of the adapter pad 400 and may have a uniform thickness along the outer surfaces of the adapter pad 400 or in other embodiments, uniform thickness within individual sections of the pad, for example, a uniform thickness in the central portion 410, a uniform thickness (possibly different or possibly the same) on one or both transverse flanges 432, 434, uniform thickness (possibly different or, possibly, the same) on one or both upwardly directed sections ah 428, 430, etc.

[00235] As best shown in FIG. 28-30, and as described above, one or both upwardly directed sections 412, 414 may include a hollow portion (s) 572 in a cavity formed between the upper and lower plates 420, 440, which is an empty space in which essentially no elastomeric material is provided, and which can create a gap within the elastomeric element 560 in the respective first and / or second upwardly directed sections 412, 414. Hollow sections 572 can provide complete separation between the elastomeric element 560 located in the central section 410, and an elastomeric element located in the transverse flanges 416, 418. In some embodiments, the void space may include a very thin layer of elastomeric material that contacts each of the upper and lower plates 420, 440 through the transition, which may result possible limitations of the tool used in the molding process, but this thin layer (if any) does not significantly affect the performance of the adapter pad 400. In addition, in some embodiments, the hollow portion 572 may include small portions of elastomeric material that extend between the upper and lower plates 420, 440, but otherwise is substantially hollow. In some embodiments, the width of the hollow portion 572 may be about 0.25 inches, or in the range of about 0.1 inches to about 0.5 inches, or at least the same as the maximum lateral and rotational movement on the adapter pad 200. In some embodiments, the hollow portion (s) 572 is configured to provide a transverse empty space between the upper and lower plates 420, 440 passing through the corresponding transition section 412, 414, so that the corresponding inner surfaces of the upper and lower plates 420, 440 in the transition section do not contact each other during transverse or rotational relative movement between them and / or due to transverse and / or rotational displacement during operation of a railway carriage with a pillow 400 adapter Located in the desired position in the rail car truck system.

[00236] As described above, the hollow portion 572 may serve to limit bending stresses in the upper and lower plates 420, 440. The hollow portion 572 may be about 0.25 inches. With a travel range of about 0.25 inches, the upwardly directed portions of the upper and lower plates 420, 440 can interact and prevent additional relative movement. This can determine the upper limit of elastomer deformation in the transverse direction and the stress of the metal.

[00237] As described above, when an adapter is used in the pillow 400, heat can be generated by friction of the pillow 400 and sliding relative to the axle box 152 of the side frame and / or relative to the bearing adapter 199; and / or hysteretic damping of the elastomeric element 560 of the adapter pad 400. These heat sources can cause an increase in the temperature of the adapter cushion, which can lead to a decrease in wear resistance and a decrease in stiffness. As described above, in some embodiments, the adapter cushion 400 may include elements that can improve its ability to reduce heat in the adapter cushion 400.

[00238] Furthermore, as described above, one or both of the outer surfaces 424 of the central portion 426 or the inner surfaces 444 of the central portion 446 may include one or more different surface elements and, in some embodiments, a pattern of surface elements in order to make these surfaces are not smooth.

[00239] As described above, in some embodiments, electrical conductivity can be provided between the upper and lower plates 420, 440. As shown in FIG. 28, a wire grounding jumper 266 can be fixed in the holes in the sides of the upper and lower plates 420, 440. Wire grounding jumper 266 can pass through the holes in the upper and lower plates 220, 240. The upper and lower plates 420, 440 may have cutouts or recesses at point 267 for crimping or securing the ground wire jumper 266 in the upper and lower plates 420, 440. In some embodiments, the wire ground wire 266 may be a stainless steel braid with a diameter of about 0.1 00 inches, but may have a diameter of just 0.050 inches.

[00240] As described above, the adapter pillow 400 may include pillows or hooks on the upper and lower adapter pillow plates 420, 440, which may be configured to position the adapter pillow 400 relative to the axle box 152 of the side frame and the bearing adapter 199, and also interact and limit the movement of the adapter pad 400 relative to the axle box 152 and the bearing adapter 199, which can focus the movement (ie, shift) of the adapter pad 400 on the elastomeric member 360. How about as described above, the connection of the adapter pillow 400 to the roller bearing adapter 199 can cause the centering of the adapter pillow 400 to center relative to the roller bearing adapter 199 and the bearing by using the vertical shoulders 106 and engaging the hooks. In addition, the adapter pad system 198 facilitates the return of the adapter 199 and the wheelset to a centered or central position with close to zero force.

[00241] As described above, the adapter pad 400 may include first and second transverse adapter hooks 270, 271. The transverse hooks 270, 271 of the adapter cushion can be integral with the bottom plate 440, including integrally with the elastomeric element 560 and / or any elastomeric coating 565 on the adapter cushion 400. As described above, the adapter cushion 400 may also include first and second lateral hooks 272, 273 of the side frame. The transverse hooks 272, 273 of the side frame can be integral with the bottom plate 440, including integrally with the elastomeric element 560 and / or elastomeric coating 565 on the adapter pad 400.

[00242] As discussed above, the elastomeric element 560 and, in particular, the external elastomeric elements 564, 566 can be made so that the rotational shear stresses of the elastomer at a displacement of up to 41 milliradians do not exceed the transverse and longitudinal shear stresses of the elastomer at a displacement of up to 0, 23 inches in the transverse direction and up to 0.14 inches in the longitudinal direction.

[00243] The elastomeric element 560 may be measured as described above with respect to other embodiments. The total shear width or transverse length of the elastomeric member 560 shown in FIG. 28-33 may be about 10 inches or in the range of about 6 inches to about 14 inches. Similarly, the total shear length or longitudinal length of the elastomeric member 560 may be about 6.9 inches, or in the range of about 6 inches to about 10 inches. The total shear perimeter or perimeter of all portions of the elastomeric member may be about 51.70 inches, or in the range of about 35 inches to about 75 inches. The total surface area of the elastomeric member 560 in the shear plane can be about 55.5 square inches or in the range of about 50 square inches to about 70 square inches. The total surface area of the elastomeric member 560 outside the central portion may be about 15.5 square inches or in the range of about 5 square inches to about 30 square inches or more than 5 square inches. Thus, the surface area of the elastomeric element in the transverse flanges 416, 418 may be about 7.75 square inches each, or in the range from about 2.5 square inches to about 15 square inches or more than 2.5 square inches.

[00244] As discussed above, in order to reduce stresses in the elastomeric element 560 at maximum shear displacement, it may be advisable to ensure normal stress or compression of the elastomeric element 560 under shear load.

[00245] For example, as discussed above, the elastomeric member 560 outside the area of the axle box 152 can be compressed by more than 0.020 inches or more than 7% of the static thickness of the elastomeric member 560. In some embodiments, pre-compression by this amount provides improved the fatigue life of the elastomeric element 560. In addition, in the embodiments discussed herein, from about 10 percent to about 30 percent of the vertical force can be distributed to each of the transverse flanges 416, 418 of the adapter pad when the vertical force acts on the central portion 410 of the adapter pad 400. In the embodiments described herein, the effect of the vertical load on the vertical shoulders 106 may provide a vertical force exceeding 3,000 pounds to pre-compress the elastomeric member.

[00246] In addition, as discussed above, the compression of the elastomeric element 560 in the area outside the axle box 152 (in the outer elastomeric elements 464, 466) can be performed by providing an elastomeric element 560 having an uneven thickness along the length of the elastomeric element 560. For example, the first and / or second outer sections 564, 566 can be formed with a thickness X, while the central section 462 can be formed with a different or smaller thickness Y. Geometry (for example, bends through upward sections 412, 414) of the upper and lower Lastin 420, 440 may be formed to conform to the differences in thickness between the X, Y, allows that the elastomeric portions in the central and external portions in contact with the inner surfaces of the upper and lower plates 420, 440, if necessary. In some embodiments, the difference in thickness of the elastomeric element forming the first and / or second outer sections 464, 466 and the central section 462 can help reduce simple shear strains of the outer layers based on the forces acting in the plane that act on the adapter pad in the longitudinal, transverse and rotational directions.

[00247] In addition, as discussed above, one or both of the transverse flanges 416, 418 can be formed so that the elastomeric layers 564, 566 in them have a thickness X that is about 0.25 inches, for example, in the range from 0, 15 inches to 0.30 inches, including all thicknesses in the range. In this embodiment, the thickness Y of the elastomeric layer 560 in the central portion 562 may be about 0.20 inches, for example, in the range of 0.15 inches to 0.25 inches, including all thicknesses in the range. The thickness of the elastomeric layers discussed herein refers to the static thickness of the elastomeric layers or the thickness of the elastomeric layers without an external load on the elastomeric layers. One or both of the transverse flange sections 564, 566 and the central section 562 can have different thicknesses, the upper sections being thinner than the central section, which can provide the desired effect, as a rule, increasing the load or compression of one or both transverse flange sections 564, 566, due to The properties of the material of the elastomeric layer additionally increase the strength and wear resistance based on the expected load during operation of a railway carriage.

[00248] Furthermore, as discussed above, and as shown in FIG. 30 and 31, the compression of the elastomeric element 560 in the transverse flanges 416, 418 can be increased by using compression gaskets in the transverse projecting flanges 416, 418. The compression gaskets can be used so that the vertical load on the vertical shoulders 106 provides vertical force, exceeding 3,000 pounds, so that from about 10 percent to about 30 percent of the vertical force is distributed to each of the transverse flanges 416, 418 of the adapter pad when exposed to a vertical Elias the central cushion portion 410 of the adapter 400. In some embodiments, compression pads can cause the distribution of most of the car’s vertical load from the central elastomeric layer 560 to the outer elastomeric layers 564, 566. As shown in FIG. 30 and 31, the first compression adapter gasket 290 may be located between the upper surface of the vertical shoulder of the roller bearing adapter 199 and the outer surface 244 of the first transverse flange 416 of the lower plate 440. The second compression adapter gasket 290 may be similarly positioned relative to the second transverse flange 418. Compression adapter gaskets 290 may have a thickness of about 0.05 inches or in the range of about 0.03 inches to about 0.18 inches. The compression gaskets discussed herein can have any number of different shapes and configurations to provide the necessary loads to compress the external elastomer. For example, compression pads can be rectangular, square, trapezoidal, pyramidal, can have a hollow cross section, and can be a plurality of compression pads. In addition, the compression pads discussed herein may be integral with the adapter pad during molding, may be integral with the roller bearing adapter, or may be added to the roller bearing adapter system after the molding process.

[00249] As discussed above, it was determined during the test that the performance of the adapter pad system 198 is a function of the stiffness of the adapter pad 400. In particular, in some embodiments, it is determined that the performance of the adapter pad, including the design life, can be improved by increasing the rigidity of the adapter pad system 198 (measured in pounds of force per inch of deformation). The physical measurement of the stiffness of the cushion can be determined as discussed previously.

[00250] Using the test methods described above, exemplary measurements and test results of the embodiments disclosed herein are shown in Table 3 below. It should be understood that these embodiments are exemplary and that other structural embodiments with other test results may exist. .

Table 3

Embodiments Described herein Normal Elastomer Area (inches2) 55.5 inch2
or about 50 inches2 to about 70 inches2 Normal elastomer area outside contact with axle box (inches2) 15.5 inch2
or about 5 inches2 to about 30 inches2 Pillow Elastomer Shear Width (Transverse Length) (inches) or from about 6 inches to about 14 inches Elastic Pillow Shear Length (Longitudinal Length) (inches) or from about 6 inches to about 10 inches Transverse stiffness
(measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) 60 thousand pounds / inch
or from about 45 thousand pounds / inch to about 80 thousand pounds / inch
or at least 45 thousand pounds / inch Longitudinal stiffness
(measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) 64 thousand pounds / inch
or from about 45 thousand pounds / inch to about 80 thousand pounds / inch
or at least 45 thousand pounds / inch Rotational stiffness
(measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) 670 thousand pounds × inch / mrad
or from about 250 thousand pounds × inch / mrad to about 840 thousand pounds × inch / mrad
or at least 250 thousand pounds × inch / mrad Vertical stiffness at least 5,000 thousand pounds per inch Transverse hysteresis (measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) or from about 3,750 pounds to about 6,250 pounds
or less than 6,000 pounds Longitudinal hysteresis
(measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) or from about 375 pounds to about 1,500 pounds
or less than 1,500 pounds Rotational hysteresis
(measured at a cycling frequency of 3 Hz and a vertical load of 35 thousand pounds) 12,000 psi
or from about 9,000 psi to about 16,000 psi
or less than 16,000 psi The shift perimeter of the Central elastomeric layer or from about 20 inches to about 30 inches The shear perimeter of the outer elastomeric layers 13.1 inches each
or about 8 to about 18 inches each The shear perimeter of the total elastomeric layer or from about 35 inches to about 75 inches Form factor of the central elastomeric layer 8.3
or from about 6 to about 10 Form Factor of External Elastomeric Layers 1.6 each
or from about 0.5 to about 3 each General form factor 4,5
or from about 2.5 to about 7

[00251] As discussed above, elastomeric layers 564, 566 outside the central portion 210 may contribute to the overall stiffness of the adapter pad 200. For example, in some embodiments, elastomeric member 560 outside the central portion 210 can provide about 15%, or in the range of about 5% to about 30% of the total lateral and longitudinal stiffness of the adapter pad, and 33%, or in the range of about 15% to about 60% of the rotational stiffness of the pillow 200 adapter.

[00252] As previously discussed, the elastomeric element 560 of the adapter pad 400, which may include an elastomeric coating 565, provides shear resistance under load in the transverse, longitudinal and rotational directions under vertical load. This shear resistance is due to the relative displacement between the upper and lower plates 420, 440 interacting through the elastomeric element 560. A simple shear strain or deformation is defined as d / t, where d is the displacement of the elastomeric element and t is the thickness of the elastomeric element. Figures 34a and 34b illustrate the lateral displacement modeling of the upper plate 420 relative to the lower plate 440 of 0.234 inches. As shown in FIG. 34a and 34b, the deformation in the transverse flanges 416, 418 is less than in the central section 410. In some embodiments, this may increase the life of the adapter pad. Furthermore, as shown in FIG. 34a and 34b, the greatest values of the deformation occur in the direction inward of the sections of the outer edges of the elastomeric section. Similarly, Figures 35a and 35b illustrate a longitudinal displacement simulation of the upper plate 420 relative to the lower plate 440 of 0.234 inches. As shown in FIG. 35a and 35b, the deformation in the transverse flanges 416, 418 is less than in the central section 410. In some embodiments, this may increase the life of the adapter pad. Furthermore, as shown in FIG. 35a and 35b, the highest strain values occur inwardly towards the outer edges of the elastomeric section.

[00253] Furthermore, in some embodiments, the shear deformation of the adapter pad 400 does not exceed 100% under conditions of maximum displacement. For example, lateral deformation may be about 74% or less than 80% or less than 90% for a lateral displacement of 0.234 inches. This strain for a lateral displacement of 0.234 inches can be about 45% less than with existing adapter pad systems. In addition, for example, the longitudinal strain may be about 72% or less than 80% or less than 90% for a longitudinal displacement of 0.139 inches. This strain for a longitudinal displacement of 0.139 inches may be about 30% less than with existing adapter pad systems.

[00254] Exemplary dimensions of an adapter pad 400 are shown and described herein; however, other dimensions may be used for the adapter pad sections, depending on the fixed dimensions of the side frame and bearings used with the particular rail carriage system.

Examples

[00255] In one example, an adapter cushion system is disclosed that is configured to accommodate a pair of wheelsets between a roller bearing and an axle box of a side frame of a railcar wagon. The adapter cushion system may include a roller bearing adapter having first and second vertical shoulders that protrude upward from the upper surface of the adapter. The adapter pillow system may also include an adapter pillow adapted to interact with the roller bearing adapter, in which the upper plate has inner and outer surfaces, a central portion, first and second upwardly extending portions protruding upward from opposing edges of the central portion, the first transverse a flange protruding outward from the first upwardly directed portion and a second transverse flange protruding outward from the second upwardly directed portion; the lower plate has inner and outer surfaces, a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upwardly extending portion, and a second transverse flange protruding outward from the second upwardly extending portion . The first and second transverse projecting flanges of the upper plate and the lower plate of the adapter pillow system can be located above the vertical shoulders of the roller bearing adapter.

[00256] The roller bearing adapter of the adapter cushion system may be cast or forged. The adapter cushion can interact with the side frame and interact with the roller bearing adapter. The upper plate of the adapter pad can interact with the side frame, so that movement between the upper plate and the side frame is limited. The lower plate of the adapter pad can interact with the roller bearing adapter, so that movement between the lower plate and the roller bearing adapter is limited. The roller bearing adapter may include longitudinal limiters configured to limit the longitudinal movement of the lower plate relative to the roller bearing adapter. Vertical shoulders may be configured to limit lateral movement of the lower plate relative to the roller bearing adapter. The upper surface of the roller bearing adapter may include a convex surface. Longitudinal stops and vertical shoulders can be configured to limit the rotational movement of the lower plate relative to the roller bearing adapter. The roller bearing adapter may be symmetrical about the transverse center line. The roller bearing adapter may be symmetrical about the longitudinal center line. The top plate of the roller bearing adapter can be continuous. The bottom plate of the roller bearing adapter can be continuous.

[00257] An adapter pad system may include an elastomeric member located between the inner surfaces of the upper plate and the lower plate. An elastomeric element located between the upper plate and the lower plate may be a plurality of elastomeric elements. The plurality of elastomeric elements may include a first external elastomeric element located between the first transverse flanges of the upper and lower plates, a second external elastomeric element located between the second transverse flanges of the upper and lower plates, and a central elastomeric element located between the central portions of the upper and lower plates . A first hollow portion may be located between the central elastomeric member and the first external elastomeric member, and a second hollow portion may be located between the central elastomeric member and the second outer elastomeric member. The first and second hollow sections may have a width of about 0.25 inches. The first and second hollow sections may be configured to limit bending stresses in the upper and lower plates. External elastomeric elements may be in a compressed state. The thickness of the external elastomeric elements can be compressed by at least 0.020 inches relative to the static state. The thickness of the external elastomeric elements can be compressed by at least 7% relative to the static state. Each of the first external elastomeric element, the second external elastomeric element, and the central elastomeric element may be substantially flat, and each may be substantially horizontal when the adapter pad is located under the axle box of the side frame of the railcar carriage. The elastomeric material may be normal to the direction of lateral displacement to increase compressive rigidity. The elastomeric material may be normal to the direction of longitudinal displacement to increase compressive stiffness. The elastomeric material may be normal to the direction of rotational displacement to increase compressive rigidity. The elastomeric material may be normal to the direction of vertical displacement to increase stiffness in compression.

[00258] The surface area of the first external elastomeric element in the sectional plane through the first external elastomeric element in the plane centered between the inner surfaces of the upper and lower plates can be more than 2.5 square inches. The surface area of the second outer elastomeric element in the section plane through the second outer elastomeric element in the plane centered between the inner surfaces of the upper and lower plates may be more than 2.5 square inches. The total surface area of the first and second external elastomeric elements in section planes through the first and second external elastomeric elements in planes centered between the inner surfaces of the upper and lower plates may be more than 5 square inches. The total surface area of the first and second external elastomeric elements in the sectional planes through the first and second external elastomeric elements in the planes centered between the inner surfaces of the upper and lower plates may be at least 10 percent of the surface area of the central elastomeric element in the sectional plane through the center of the central an elastomeric element in a plane centered between the inner surfaces of the upper and lower plates.

[00259] The central elastomeric element may form a plurality of gaps that form a plurality of gaps in the elastomeric element located between the central portion of the upper plate and the central portion of the lower plate. The plurality of gaps may have a thickness less than the total distance between the upper plate and the lower plate, and the portion of the elastomeric element is vertically relative to one or more of the many gaps and is in contact with one or both of the upper and lower plates.

[00260] The central elastomeric element can form an outer edge, wherein, in a plan view, one or more portions of the outer edge are curved. At least a portion of the outer edge of the central elastomeric portion may have an inwardly inward contour. The first and second outer elastomeric elements can form an outer edge, and in the top view one or more sections of the outer edge are curved. One or more sections of the outer edges of the elastomeric elements may have a continuous radius, measured from the center point of the central portion of the upper plate. Any edge of the elastomeric element may have a contour recessed inward.

[00261] One or both of the first and second outer elastomeric elements may form an outer edge, one or both of the first and second transverse flanges of the upper and lower plates extending outward at least beyond a portion of the outer edge in the respective first and second transverse flanges.

[00262] The adapter pad may include an elastomeric member located between the outer surfaces of the first and second transverse flanges of the bottom plate and the vertical shoulders of the roller bearing adapter.

[00263] At least a portion of the outer edges of the elastomeric elements may have an inwardly-contoured contour. An inwardly recessed contour may be formed by a first linear portion that extends from a location near the inner surface of the upper plate, and a second linear portion that extends from a location near the inner surface of the upper plate. The first and second linear sections can be connected to a transition that extends between the first and second linear sections. Each of the first and second linear sections may extend from a nearby corresponding upper or lower plate at an angle in the range of about 25 degrees to about 35 degrees to a plane extending over the surface of the corresponding upper or lower plate from which the corresponding linear section extends.

[00264] The first and second external elastomeric elements may have the same thickness or greater thickness than the central elastomeric element. The thickness of the first and second outer elastomeric elements can range from about 0.15 inches to about 0.30 inches. The thickness of the central elastomeric element may range from about 0.15 inches to about 0.25 inches. The thickness of the adapter cushion can range from about 0.4 inches to about 0.8 inches.

[00265] The adapter cushion system may also include an elastomeric layer located above the outer surface of the upper plate, and / or may include an elastomeric layer located below the outer surface of the lower plate. The elastomeric layer may cover the entire outer surface of the adapter pad or portions thereof. The upper and lower plates of the adapter cushion may have uneven thickness. The upper and lower plates may have uniform thickness. The top plate may have uneven thickness. The top plate may have uniform thickness. The bottom plate may have uneven thickness. The bottom plate may have uniform thickness.

[00266] The adapter cushion system may be configured to return to a neutral or central position in the axle box opening of the side frame after termination of the load.

[00267] The first and second transverse flanges of the upper plate may include a flat outer surface that may be parallel to the outer surface of the central portion of the upper plate.

[00268] The inner surfaces of each of the first and second upwardly directed portions of the first and second adapter cushion plates may include a flat portion. The inner surfaces of each of the first and second upwardly directed portions of the first and second adapter pad plates may include a curved portion. The first and second upwardly directed portions of the first and second adapter cushion plates may include at least a portion that extends at an obtuse angle to a plane extending over the outer surface of the central portion of the upper plate.

[00269] The first and second transverse flanges of the upper plate of the adapter pad may include exposed outer surfaces on which the adapter pad is in contact with the axle box opening of the side frame. The first and second transverse flanges may be in contact with air from the outside of the envelope curve of the axle box opening of the side frame. The first and second transverse flanges may be configured to reduce the heat of the adapter cushion. The first and second transverse flanges may be configured to reduce the heat of the adapter pad system.

[00270] The adapter cushion may have a transverse length of the central portion, which may be equal to the distance between the side walls of the axle box surface. The transverse length of the center portion may be about 0.125 inches longer than the length between the side walls of the side frame on the surface of the axle box. The total transverse length of the top plate may be at least 7.5 inches.

[00271] The adapter pillow system may also include a first transverse adapter hook located between the inner surface of the first vertical shoulder of the roller bearing adapter and the first upwardly directed portion of the bottom plate; and a second transverse adapter hook located between the inner surface of the second vertical shoulder of the roller bearing adapter and the second upwardly directed portion of the lower plate. The first and second transverse hooks of the adapter can be made of elastomeric material. The first and second transverse hooks of the adapter can be configured to limit sliding or relative movement between the adapter of the roller bearing and the outer surface of the lower plate of the adapter cushion. The first and second transverse hooks of the adapter can be arranged to center the lower plate of the adapter cushion on the roller bearing adapter.

[00272] The adapter cushion system may also include a first lateral hook of the side frame located on the outer surface of the first upwardly directed portion of the upper plate; and a second lateral hook of the side frame located on the outer surface of the second upwardly directed portion of the upper plate. A first transverse hook of the side frame may be located between the outer surface of the first transverse flange of the upper plate and the axle box of the side frame, and a second transverse hook of the side frame may be located between the outer surface of the second transverse flange of the upper plate and box of the side frame. The first and second transverse hooks of the side frame can be made of elastomeric material. The first and second transverse hooks of the side frame can be configured to limit sliding or relative movement between the outer surface of the upper plate and the side frame directly above the axle box.

[00273] In some examples, the adapter pad system may be configured to limit the temperature of the elastomer below the degradation temperature of a particular elastomeric and / or adhesive material used in the construction of the pad. The adapter pad system can also be configured to reduce melting of the elastomeric element.

[00274] The adapter pillow system may include a first adapter compression pad located between the upper surface of the first vertical shoulder of the roller bearing adapter and the outer surface of the first transverse flange of the lower plate. The adapter pillow system may also include a second adapter compression pad located between the upper surface of the second vertical shoulder of the roller bearing adapter and the outer surface of the second transverse flange of the lower plate. The thickness of the first and second compression adapter gaskets may range from about 0.06 inches to about 0.18 inches.

[00275] The adapter pad may include a lower first compression pad of the adapter pad located between the elastomeric member and the first transverse flange of the bottom plate. The adapter pad may also include a second lower compression pad of the adapter pad located between the elastomeric member and the second transverse flange of the bottom plate. The thickness of the first and second lower compression pads of the adapter pad may range from about 0.06 inches to about 0.18 inches.

[00276] The adapter pad may include a first upper compression pad of the adapter pad located between the first transverse flange of the upper plate and the first external elastomeric member. The adapter pad may also include a second upper compression pad of the adapter pad located between the second transverse flange of the upper plate and the second outer elastomeric member. The thickness of the first and second upper compression pads of the adapter pad may range from about 0.06 inches to about 0.18 inches.

[00277] Compression gaskets can be configured to provide a vertical compressive load of at least 3,000 pounds on external elastomeric elements when exposed to a vertical load of 35,000 pounds on the central portions of the adapter pad. Compression gaskets can be rectangular. Compression gaskets may have a rectangular cross-sectional shape, a curved cross-sectional shape, a triangular cross-sectional shape, or a trapezoidal cross-sectional shape. Compression gaskets may include a raised portion. Compression gaskets may include a hollow portion. Compression gaskets may include a plurality of compression gaskets.

[00278] The transverse flanges of the adapter pad may be vertically supported on the vertical shoulders of the roller bearing adapter. From about 10 percent to about 30 percent of the vertical force can be distributed to each of the transverse flanges of the adapter pad when the vertical force is applied to the central portions of the adapter pad. The effect of vertical loading on the vertical shoulders can provide a vertical force of at least 3,000 pounds to pre-compress the elastomeric member.

[00279] The upper plate, lower plate and elastomeric element of the adapter pad together can provide longitudinal stiffness, which can be at least 45,000 pounds per inch, with a longitudinal displacement of the upper plate relative to the lower plate to 0.139 inches from a central position when exposed to vertical load of 35,000 pounds to the central portions of the adapter pad. The longitudinal hysteresis of the adapter pad system can be less than about 1,500 pounds.

[00280] The upper plate, lower plate and elastomeric element of the adapter pad together can provide lateral stiffness, which can be at least 45,000 pounds per inch, with a lateral displacement of the upper plate relative to the lower plate to 0.234 inches from a central position when exposed to vertical load of 35,000 pounds to the central portions of the adapter pad. The lateral displacement hysteresis of the adapter pad system can be less than about 6,000 pounds.

[00281] The upper plate, lower plate and elastomeric element of the adapter cushion can provide rotational stiffness, which can be at least 250,000 pounds per inch per radian of rotation, with a rotational displacement of the upper plate relative to the lower plate to 41 milliradians from a central position when exposed 35,000 pounds of vertical load on the center sections of the adapter cushion. Torsion hysteresis can be less than about 16,000 psi.

[00282] The upper plate, lower plate and elastomeric element of the adapter pad can provide vertical stiffness, which can be at least 5,000,000 pounds per inch with a vertical offset of 0.05 inches. The vertical displacement can be non-linear and can range from 5,000,000 pounds per inch to 30,000,000 pounds per inch depending on changes in durometer hardness, thickness tolerances and non-linear stiffness in compression.

[00283] The upper plate, the lower plate and the elastomeric element of the adapter pad together can provide lateral stiffness, which is about ten percent of the longitudinal rigidity when vertical loads are applied to the central portions of the adapter pad.

[00284] The upper plate, the lower plate and the elastomeric element of the adapter pad together can provide lateral deformation in the elastomeric element, which is essentially the same throughout the elastomeric element when a vertical load is applied to the central portions of the adapter pad.

[00285] The upper plate, the lower plate and the elastomeric element of the adapter cushion can together provide longitudinal deformation in the elastomeric element, which is essentially the same throughout the elastomeric element when a vertical load is applied to the central portions of the adapter cushion.

[00286] The upper plate, the lower plate and the elastomeric element of the adapter cushion can together provide rotational deformation in the elastomeric element, which can be substantially the same throughout the elastomeric element when a vertical load is applied to the central portions of the adapter cushion.

[00287] The upper plate, lower plate and elastomeric element of the adapter pad can together provide a rotational deformation that is less than or equal to lateral deformation at any point of the elastomeric element when a vertical load is applied to the central portions of the adapter pad.

[00288] The upper plate, the lower plate and the elastomeric element of the adapter pad together can provide a shear strain that does not exceed 120% at maximum displacement.

[00289] The thickness of the central portion of the bottom plate of the adapter pad may be uneven. The thickness of the central portion of the bottom plate may be greater at the transverse edges than in the center of the central portion.

[00290] The thickness of the elastomeric element located between the central sections of the upper and lower plates can be substantially uniform.

[00291] In another example, a method of forming an adapter pad may include providing a top plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first directional an upward transverse section, and a second transverse flange protruding outward from the second upwardly directed transverse section; providing a lower plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upward transverse portion, and a second transverse flange protruding outward from the second upward transverse section; inserting an elastomeric element between the upper plate and the lower plate, wherein the first external elastomeric element is placed between the first transverse flanges, the second external elastomeric element is placed between the second transverse flanges, and the central elastomeric element is placed between the central sections; compressing the first transverse flange of the upper plate and the first transverse flange of the lower plate towards each other; and compressing the second transverse flange of the upper plate and the second transverse flange of the lower plate towards each other.

[00292] The compression steps may cause deformation of the first and second transverse flanges after completion of the molding operation. This deformation may result in preloading of the external elastomeric elements. During compression steps, a compression force of more than 3,000 pounds may be applied to the external elastomeric elements. In the compression steps, the external elastomeric element can be compressed by at least 0.02 inches relative to the static thickness of the external elastomeric elements. In the compression steps, the external elastomeric element is compressed by more than 7 percent of the static thickness of the external elastomeric elements.

[00293] In another example, a method for forming an adapter pad may include providing a top plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, and a first transverse flange protruding outward and downward from a first upward transverse section, and a second transverse flange protruding outward and downward from a second upward transverse section; providing a lower plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward and upward from the first upward transverse portion, and a second transverse flange protruding outward and upward from the second directional upward transverse section; inserting an elastomeric element between the upper plate and the lower plate; and compressing the upper plate and the lower plate so that the transverse portions of the upper and lower plates are substantially parallel.

[00294] In the compression steps, the external elastomeric element can be compressed at least 0.02 inches from the static thickness of the external elastomeric elements. In the compression steps, the external elastomeric element can compress more than 7 percent of the static thickness of the external elastomeric elements.

[00295] In another example, a method of forming an adapter pad may include providing a top plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first directional an upward transverse section, and a second transverse flange protruding outward from the second upwardly directed transverse section; providing a lower plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upward transverse portion, and a second transverse flange protruding outward from the second upward transverse section; inserting a first external elastomeric element between the first transverse flange of the upper plate and the first transverse flange of the lower plate; inserting a second outer elastomeric element between the second transverse flange of the upper plate and the second transverse flange of the lower plate; and inserting a central elastomeric element between the central portion of the upper plate and the central portion of the lower plate.

[00296] The thickness of the central elastomeric element may be less than or equal to the thickness of the first and second external elastomeric elements.

[00297] In another example, a method for forming an adapter pad may include providing a top plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first directional an upward transverse section, and a second transverse flange protruding outward from the second upwardly directed transverse section; providing a lower plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upward transverse portion, and a second transverse flange protruding outward from the second upward transverse section; inserting a first external elastomeric element between the first transverse flange of the upper plate and the first transverse flange of the lower plate; inserting a second outer elastomeric element between the second transverse flange of the upper plate and the second transverse flange of the lower plate; inserting a central elastomeric element between a central portion of the upper plate and a central portion of the lower plate; compressing the first and second transverse flanges of the upper plate and the lower plate together; and fastening the upper plate to a first external elastomeric element, a second external elastomeric element and a central elastomeric element.

[00298] The thickness of the central elastomeric element may be less than the thickness of the first and second external elastomeric elements.

[00299] In the compression steps, the external elastomeric element can be compressed by at least 0.02 inches relative to the static thickness of the external elastomeric elements. In the compression steps, the external elastomeric element is compressed by more than 7 percent of the static thickness of the external elastomeric elements.

[00300] In another example, an adapter pillow system is disclosed for use between an axle box opening of a side frame of a railway carriage and a roller bearing adapter of an axis of a railway carriage. The axle box opening of the side frame may form a first outer side opposite the second outer side and an axle box located and extending between the first outer side and the second outer side. The adapter pillow system may include a bearing adapter forming the lower surface and the upper surface, the lower surface being mounted on a roller bearing of the axis of the railway carriage, the upper surface forming opposing first and second vertical shoulders that protrude upward from the upper surface, on each side of the side frame slightly above the axle box. The adapter pillow system may include an adapter pillow adapted to interact with the bearing adapter, including an upper plate having inner and outer surfaces, a central portion, first and second upwardly extending portions protruding upward from opposing edges of the central portion, the first transverse a flange protruding outward from the first upwardly directed portion and a second transverse flange protruding outward from the second upwardly directed portion; and a lower plate having inner and outer surfaces, a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upwardly directed portion, and a second transverse flange protruding outward from the second directional up plot.

[00301] The central portions of the upper plate and the lower plate can be located under the axle box of the axle box side opening of the side frame, and the first and second laterally projecting flanges of the upper plate and lower plate can be located above the vertical shoulders of the roller bearing adapter and outside the axle box of the axle box the opening of the side frame and along the first and second outer sides of the axle box opening of the side frame.

[00302] In another example, an adapter cushion is disclosed that is adapted to be placed between the adapter and the axle box of the side frame of a railcar bogie. The adapter cushion may include an upper plate having inner and outer surfaces, a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upwardly directed portion, and a second transverse flange, protruding outward from the second upwardly directed portion; and a lower plate having inner and outer surfaces, a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upwardly directed portion, and a second transverse flange protruding outward from the second directional up plot.

[00303] The outer surfaces of the first and second transverse projecting flanges of the lower plate may be vertically above the outer surface of the central portion of the upper plate.

[00304] In another example, a method for forming an adapter pad may include providing a top plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first directional an upward transverse section, and a second transverse flange protruding outward from the second upwardly directed transverse section; providing a lower plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upward transverse portion, and a second transverse flange protruding outward from the second upward transverse section; inserting a first external elastomeric element between the first transverse flange of the upper plate and the first transverse flange of the lower plate; inserting a second outer elastomeric element between the second transverse flange of the upper plate and the second transverse flange of the lower plate; inserting a central elastomeric element between a central portion of the upper plate and a central portion of the lower plate; curing or curing the elastomeric elements; insert the first compression gasket into the first transverse flange; and insert the second compression gasket into the second transverse flange. In some embodiments, compression pads may be added after curing or curing of the elastomer.

[00305] In another example, a method for forming an adapter pad may include providing a top plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first directional an upward transverse section, and a second transverse flange protruding outward from the second upwardly directed transverse section; providing a lower plate having a central portion, first and second upwardly extending portions protruding upward from opposite edges of the central portion, a first transverse flange protruding outward from the first upward transverse portion, and a second transverse flange protruding outward from the second upward transverse section; inserting a first external elastomeric element between the first transverse flange of the upper plate and the first transverse flange of the lower plate; inserting a second outer elastomeric element between the second transverse flange of the upper plate and the second transverse flange of the lower plate; inserting a central elastomeric element between a central portion of the upper plate and a central portion of the lower plate; curing elastomeric elements; insert the first compression gasket into the first transverse flange; and insert the second compression gasket into the second transverse flange. The steps of inserting the first and second compression gaskets can be performed after curing the elastomeric elements.

[00306] In the compression steps, the external elastomeric element can be compressed by at least 0.02 inches relative to the static thickness of the external elastomeric elements. In the compression steps, the external elastomeric element is compressed by more than 7 percent of the static thickness of the external elastomeric elements.

[00307] In another example, an adapter pillow system is disclosed for use between an axle box of a side frame of a railroad pasture and a roller bearing of an axis of a railroad car. The axle box opening of the side frame may form a first outer side opposite the second outer side and an axle box located and extending between the first outer side and the second outer side. The adapter cushion system may include a bearing adapter forming a lower surface and an upper surface, the lower surface being mounted on a roller bearing of an axis of a railway carriage. The adapter cushion may be configured to interact with the bearing adapter and may further include an upper plate having inner and outer surfaces, a central portion and outer portions; a lower plate having inner and outer surfaces, a central portion and outer portions, and an elastomeric element having a central portion and outer portions located between the inner surfaces of the upper and lower plates.

[00308] The central portions of the upper plate and the lower plate can be located under the axle box of the axle box side opening, and the outer portions of the upper and lower plates can be located outside the axle box of the axle box of the side frame.

[00309] An adapter pad system may include a continuous top plate. The adapter pad system may include a continuous bottom plate.

[00310] The total surface area of the outer sections of the elastomeric element in the section planes through the outer sections of the elastomeric elements in planes centered between the inner surfaces of the upper and lower plates may be more than 5 square inches.

[00311] The total surface area of the outer sections of the elastomeric elements in the sectional planes through the outer sections of the elastomeric elements in the planes centered between the inner surfaces of the upper and lower plates can be at least 10 percent of the surface area of the central portion of the elastomeric element in the sectional plane through the center of the center plot elastomeric element in a plane centered between the inner surfaces of the upper and lower plates.

[00312] The central portion of the elastomeric member may lie in a different plane than the outer portions of the elastomeric member. The central portion of the elastomeric member may lie in a plane parallel to the outer portions of the elastomeric member. External sections can be vertically spaced from the central sections.

[00313] The upper plate can interact with the side frame, and the lower plate can interact with the roller bearing adapter.

[00314] In another example, an adapter cushion system is disclosed for use between an axle box of a side frame of a railroad pasture and a roller bearing of an axis of a railroad car. The axle box opening of the side frame may form a first outer side opposite the second outer side and an axle box located and extending between the first outer side and the second outer side. The adapter cushion system may include a bearing adapter forming a lower surface and an upper surface, the lower surface being mounted on a roller bearing of an axis of a railway carriage. The adapter pillow system may include an adapter pillow configured to interact with the bearing adapter, which includes an upper plate having inner and outer surfaces, a central portion and outer portions; a lower plate having inner and outer surfaces, a central portion and outer portions, and an elastomeric element having a central portion and outer portions located between the inner surfaces of the upper and lower plates.

[00315] The central portions of the upper plate and the lower plate can be located under the axle box of the axle box side opening, and the outer sections of the upper and lower plates can be located outside the axle box of the axle box side opening.

[00316] The outer sections of the upper and lower plates may be configured to receive from about 10 percent to about 30 percent of the vertical force acting on the central sections.

[00317] The outer portions of the adapter pad may be supported by the vertical shoulders of the bearing adapter.

[00318] In another example, a roller bearing adapter is disclosed adapted to be placed between a roller bearing and a pillow of an adapter of a railcar carriage. The roller bearing adapter may have a bearing surface, a convex surface of the adapter, a longitudinal center line, and first and second vertical shoulders that protrude upward from the axial convex surface of the adapter. The thickness of the central portion of the roller bearing adapter can be less than 0.75 inches when measured along a longitudinal center line from the bearing surface to the axle box convex surface of the adapter.

[00319] The thickness of the roller bearing adapter can be approximately 0.60 to 0.75 inches when measured along a longitudinal center line from the abutment surface to the axle box convex surface of the adapter. The width of the vertical shoulders may be at least 0.5 inches.

[00320] The roller bearing adapter may have a moment of inertia in the longitudinal axis of the roller bearing adapter around the transverse axis about 5.2 inches above the center axis of the axis, which is about 1.4 inches ^4, or in the range of about 1.0 to about 2.0 inch ⁴ . The transverse axis may range from about 5.0 inches to about 5.5 inches from the center axis of the axis. The roller bearing adapter may have a moment of inertia of the cross section along the longitudinal axis of the roller bearing adapter around a vertical axis in the center of the adapter, which may be about 86.8 inches ⁴ or in the range of about 50 to about 100 inches ⁴ .

[00321] The present invention is disclosed above and in the accompanying drawings with reference to many examples. However, the purpose of the disclosure is to provide examples of various features and concepts associated with the invention, and not to limit the scope of protection of the invention. The expressions and descriptions used herein are for illustrative purposes only and are not intended to be limiting. One skilled in the art will appreciate that numerous changes and modifications can be made to the examples described above without departing from the scope of protection of the present invention. For example, the steps of the methods need not be performed in a specific order, unless indicated, although they may be listed in that order in the disclosure.

Claims (74)

1. Pillow adapter roller bearing, made with the possibility of use with a three-element trolley having geometry according to the AAR standard, and the pillow adapter is made with the possibility of interaction with axle box arch of the side frame, and the pillow adapter contains: a continuous upper plate having a central portion, first and second upwardly extending portions protruding upward from opposing edges of the central portion, a first transverse flange protruding outward from the first upward directed portion, the first transverse flange having a first transverse edge and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, the continuous upper plate having first and second longitudinal edges; a continuous lower plate having a central portion, first and second upwardly extending portions protruding upward from opposing edges of the central portion, a first transverse flange protruding outward from the first upward directed portion, the first transverse flange having a first transverse edge, and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, the continuous lower plate having first and second longitudinal edges; an elastomeric element located between the upper and lower plates; wherein the first transverse edge of the upper plate and the second transverse edge of the upper plate form a side bent inwardly or angled inwardly from the outer surface of the upper plate to the inner surface of the upper plate in a side view and the first transverse edge of the lower plate and the second transverse edge of the lower plate form or an edge directed at an angle inward from the outer surface of the lower plate to the inner surface of the lower plate in side view; moreover, the first longitudinal edge of the upper plate and the second longitudinal edge of the upper plate form a bend inward or angled inwardly from the outer surface of the upper plate to the inner surface of the upper plate in side view and the first longitudinal edge of the lower plate and the second longitudinal edge of the lower plate form a bend inward or a side directed at an angle inward from the outer surface of the bottom plate to the inner surface of the bottom plate in side view; moreover, the first transverse edge of the upper plate and the second transverse edge of the upper plate contain curved sections in a plan view and the first transverse edge of the lower plate and the second transverse edge of the lower plate contain curved sections in a plan view; while the elastomeric element extends outward in the transverse direction beyond the first and second transverse edges of the upper and lower plates; and the elastomeric element extends outwardly in the longitudinal direction beyond the first and second longitudinal edges of the upper and lower plates. 2. A pillow according to claim 1, in which the first transverse edge of the upper plate and the second transverse edge of the upper plate have a continuous radius in a plan view, measured from the vertical axis at the center point of the central portion of the upper plate, the first transverse edge of the lower plate and the second transverse edge the bottom plate have a continuous radius in a plan view, measured from the vertical axis at the center point of the central portion of the bottom plate. 3. A pillow according to claim 1, in which the elastomeric element extends outward in the transverse direction beyond the first and second transverse edges of the upper and lower plates by at least 0.05 inches. 4. A pillow according to claim 1, in which the elastomeric element extends outward in the longitudinal direction beyond the first and second longitudinal edges of the upper and lower plates by at least 0.05 inches. 5. A pillow according to claim 1, in which a section of an elastomeric element located between the central sections of the upper and lower plates has a substantially uniform thickness. 6. A cushion system for a roller bearing adapter adapted to be used with a three-piece trolley having AAR geometry, comprising: a roller bearing adapter configured to interact with a roller bearing, the roller bearing adapter comprising: convex upper surface; a lower surface configured to interact with a roller bearing; and first and second vertical shoulders that protrude upward from opposing transverse edges of the upper surface; an adapter cushion that interacts with a roller bearing adapter and is configured to interact with the axle box of the side frame, wherein the adapter cushion comprises: a continuous upper plate having a central portion, first and second upwardly extending portions protruding upward from opposing edges of the central portion, a first transverse flange protruding outward from the first upward directed portion, the first transverse flange having a first transverse edge and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, the continuous upper plate having first and second longitudinal edges; a continuous lower plate having a central portion, first and second upwardly extending portions protruding upward from opposing edges of the central portion, a first transverse flange protruding outward from the first upward directed portion, the first transverse flange having a first transverse edge, and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, the continuous lower plate having first and second longitudinal edges; and an elastomeric element located between the upper and lower plates; the first and second laterally projecting flanges of the upper plate and lower plate are completely located above the vertical shoulders of the roller bearing adapter. 7. The system according to claim 6, in which the first transverse edge of the upper plate and the second transverse edge of the upper plate contain curved sections in a plan view and the first transverse edge of the lower plate and the second transverse edge of the lower plate contain curved sections in a plan view. 8. The system of claim 7, wherein the first transverse edge of the upper plate and the second transverse edge of the upper plate have a continuous radius in a plan view, measured from a vertical axis at a center point of a central portion of the upper plate, and wherein the first transverse edge of the lower plate and the second the transverse edge of the bottom plate has a continuous radius in a plan view, measured from the vertical axis at the center point of the central portion of the bottom plate. 9. The system according to claim 6, in which the first transverse edge of the upper plate and the second transverse edge of the upper plate form an inwardly curved or angled inward edge from the outer surface of the upper plate to the inner surface of the upper plate in side view, the first transverse edge of the lower plate and the second transverse edge of the lower plate forms a side bent inwardly or angled inwardly from the outer surface of the lower plate to the inner surface of the lower plate in a side view. 10. The system according to claim 6, in which the first longitudinal edge of the upper plate and the second longitudinal edge of the upper plate form a bend inward or angled inwardly from the outer surface of the upper plate to the inner surface of the upper plate in side view, the first longitudinal edge of the lower plate and the second longitudinal edge of the lower plate forms a side bent inwardly or angled inwardly from the outer surface of the lower plate to the inner surface of the lower plate in a side view. 11. The system according to claim 6, in which the elastomeric element extends outward in the transverse direction beyond the first and second transverse edges of the upper and lower plates. 12. The system of claim 6, wherein the elastomeric element extends outward in a longitudinal direction beyond the first and second longitudinal edges of the upper and lower plates. 13. The system of claim 6, wherein the largest strain values occur inwardly toward the outer edges of the elastomeric member when the upper plate is offset from the bottom plate by 0.234 inches in the transverse direction. 14. The system of claim 6, wherein the upper plate, lower plate, and elastomeric element of the adapter pad jointly provide a deformation of less than 80% when the upper plate is offset from the bottom plate by 0.234 inches in the transverse direction. 15. The system of claim 6, wherein the upper plate, lower plate and elastomeric element of the adapter pad jointly provide a deformation of less than 90% when the upper plate is offset from the bottom plate by 0.234 inches in the transverse direction. 16. The system of claim 6, wherein the largest strain values occur inwardly toward the outer edges of the elastomeric member when the upper plate is offset 0.139 inches in the longitudinal direction from the bottom plate. 17. The system of claim 6, wherein the upper plate, lower plate and elastomeric element of the adapter pad jointly provide a deformation of less than 80% when the upper plate is offset by 0.139 inches in the longitudinal direction. 18. The system of claim 6, wherein the upper plate, lower plate and elastomeric element of the adapter pad jointly provide a deformation of less than 90% when the upper plate is offset by 0.139 inches in the longitudinal direction. 19. The system according to claim 6, in which the thickness of the sections of elastomeric elements located between the first and second transverse flanges of the upper and lower plates is pre-compressed relative to the static state. 20. The system of claim 6, wherein the elastomeric element further comprises: a first compression pad located between the first transverse flange of the lower plate and the first vertical shoulder of the roller bearing adapter; and a second compression pad located between the second transverse flange of the lower plate and the second vertical shoulder of the roller bearing adapter. 21. The system of claim 6, wherein the portion of the elastomeric member located between the central portions of the upper and lower plates has a substantially uniform thickness. 22. Pillow adapter roller bearing, made with the possibility of using a three-element trolley having geometry according to the AAR standard, and the pillow adapter is made with the possibility of interaction with the axle box of the side frame, and the pillow adapter contains: a continuous upper plate having a central portion, first and second upwardly extending portions protruding upward from opposing edges of the central portion, a first transverse flange protruding outward from the first upward directed portion, the first transverse flange having a first transverse edge and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, the continuous upper plate having first and second longitudinal edges; a continuous lower plate having a central portion, first and second upwardly extending portions protruding upward from opposing edges of the central portion, a first transverse flange protruding outward from the first upward directed portion, the first transverse flange having a first transverse edge, and a second transverse flange protruding outward from the second upwardly directed portion, the second transverse flange having a second transverse edge, the continuous lower plate having first and second longitudinal edges; and an elastomeric element located between the upper and lower plates; wherein the first transverse edge of the upper plate and the second transverse edge of the upper plate form a side bent inwardly or angled inwardly from the outer surface of the upper plate to the inner surface of the upper plate in side view, the first transverse edge of the lower plate and the second transverse edge of the lower plate form inwardly or angled inwardly the edge from the outer surface of the lower plate to the inner surface of the lower plate in side view; and moreover, the first longitudinal edge of the upper plate and the second longitudinal edge of the upper plate form a side bent inward or angled inward from the outer surface of the upper plate to the inner surface of the upper plate in side view, the first longitudinal edge of the lower plate and the second longitudinal edge of the lower plate form or an edge directed at an angle inward from the outer surface of the lower plate to the inner surface of the lower plate in side view. 23. A pillow according to claim 22, in which the first transverse edge of the upper plate and the second transverse edge of the upper plate contain curved sections in a plan view, wherein the first transverse edge of the lower plate and the second transverse edge of the lower plate contain curved sections in a plan view. 24. A pillow according to claim 23, in which the first transverse edge of the upper plate and the second transverse edge of the upper plate have a continuous radius in a plan view, measured from the vertical axis at the center point of the central portion of the upper plate, the first transverse edge of the lower plate and the second transverse edge the bottom plate have a continuous radius in a plan view, measured from the vertical axis at the center point of the central portion of the bottom plate. 25. A pillow according to claim 24, wherein any point on the transverse edge when the upper plate rotates relative to the lower plate to 41 milliradians from the neutral position has a linear displacement of less than or equal to 0.234 inches. 26. A pillow according to claim 22, in which the elastomeric element extends outward in the transverse direction beyond the first and second transverse edges of the upper and lower plates, the elastomeric element extends outward in the longitudinal direction beyond the first and second longitudinal edges of the upper and lower plates. 27. Pillow according to claim 22, in which the thickness of the sections of elastomeric elements located between the first and second transverse flanges of the upper and lower plates is pre-compressed relative to the static state. 28. A pillow according to claim 22, in which the elastomeric element further comprises: a first compression pad located under the first transverse flange of the bottom plate; and a second compression gasket located under the second transverse flange of the bottom plate. 29. The pillow of claim 22, wherein the portion of the elastomeric member located between the central portions of the upper and lower plates has a substantially uniform thickness. 30. The pillow of claim 22, wherein the adapter pillow has a total longitudinal length of from about 6.5 inches to about 8.5 inches, wherein the adapter pillow has a total transverse length of from about 9 inches to about 11 inches. 31. A pillow according to claim 22, in which the elastomeric element has a Shore durometer hardness of 65 to 80 on a scale A. 32. A cushion system for a roller bearing adapter adapted to be used with a three-piece trolley having AAR geometry, comprising: a roller bearing adapter configured to interact with a roller bearing, the roller bearing adapter comprising: top surface; and a lower surface configured to interact with a roller bearing; an adapter cushion that interacts with a roller bearing adapter and is configured to interact with the axle box of the side frame, wherein the adapter cushion comprises: top plate; bottom plate; and an elastomeric element located between the upper and lower plates; wherein the upper plate, lower plate and elastomeric member together provide a longitudinal stiffness of at least 45,000 pounds per inch, with a longitudinal displacement of the upper plate relative to the lower plate to 0.139 inches from a central position, a transverse stiffness of at least 45,000 pounds per inch, with a lateral displacement of the upper plate relative to the lower plate to 0.234 inches from the center position, and a rotational stiffness of at least 250,000 psi per radian of rotation, p With a rotational displacement of the top plate relative to the bottom plate up to 41 milliradians from a central position when a vertical load of 35,000 pounds is applied to the central portions of the adapter pad. 33. The system according to p. 32, in which the highest values of deformation occur in the direction inward of the outer edges of the elastomeric element when the upper plate is offset from the lower plate by 0.234 inches in the transverse direction. 34. The system of claim 32, wherein the upper plate, lower plate and elastomeric element of the adapter pad jointly provide a deformation of less than 90% when the upper plate is offset from the bottom plate by 0.234 inches in the transverse direction. 35. The system according to p. 32, in which the highest values of deformation occur in the direction inward of the outer edges of the elastomeric element when the upper plate is offset from the lower plate by 0.139 inches in the longitudinal direction. 36. The system of claim 32, wherein the upper plate, lower plate, and elastomeric element of the adapter pad jointly provide a deformation of less than 90% when the upper plate is offset by 0.139 inches in the longitudinal direction. 37. The system of claim 32, wherein the elastomeric member further comprises: a first compression pad located under the first transverse flange of the bottom plate; and a second compression gasket located under the second transverse flange of the bottom plate. 38. The system of claim 32, wherein the portion of the elastomeric member located between the central sections of the upper and lower plates has a substantially uniform thickness.

Images